Valve having integrated pressure assist mechanism

ABSTRACT

A valve is provided including a first valve member and a second valve member. The first valve member includes a first step and a first orifice adjacent the first step. The second valve member includes a second step and a second orifice adjacent the second step. The second valve member is movable relative to the first valve member between an open position, in which the first orifice is fluidly connected the second orifice, and a closed position, in which the first orifice is substantially fluidly disconnected from the second orifice. The first and second steps are fluidly connected to the second orifice and substantially fluidly disconnected from the first orifice when the second valve member is in the closed position, and the first and second steps are fluidly connected to the first and second orifices when the second valve member is in the open position.

CROSS REFERENCE TO RELATED APPLICATIONS

This application claims priority to U.S. provisional patent application61/058,083, filed Jun. 2, 2008, which is incorporated by reference inits entirety.

BACKGROUND

A hydraulic system may include multiple hydraulic loads, each of whichmay have different flow and pressure requirements that can vary overtime. The hydraulic system may include a pump for supplying a flow ofpressurized fluid to the hydraulic loads. The pump may have a variableor fixed displacement configuration. Fixed displacement pumps are oftensmaller, lighter, and less expensive than variable displacement pumps.Generally, fixed displacement pumps deliver a definite volume of fluidfor each cycle of pump operation. The output volume of a fixeddisplacement pump can be controlled by adjusting the speed of the pump.Closing or otherwise restricting the outlet of a fixed displacement pumpwill cause a corresponding increase in the system pressure. To avoidover pressurizing the hydraulic system, fixed displacement pumpstypically utilize a pressure regulator or an unloading valve to controlthe pressure level within the system during periods in which the pumpoutput exceeds the flow requirements of the multiple hydraulic loads.The hydraulic system may further include various valves for controllingthe distribution of the pressurized fluid to the multiple loads.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1A is a side cross-sectional view of an exemplary valve manifoldincluding a main-stage manifold and a pilot valve manifold.

FIG. 1B is an enlarged view of a portion of the main-stage manifold inFIG. 1A.

FIG. 1C is an enlarged view of a portion of the main-stage manifold inFIG. 1A.

FIG. 2A is an illustration of an exemplary main-stage manifold employingmultiple main-stage valves arranged in a co-parallel configuration.

FIG. 2B is a schematic illustration of the co-parallel valveconfiguration in FIG. 2A.

FIG. 3A is an illustration of exemplary main-stage manifold employingmultiple main-stage valves arranged in a radial configuration.

FIG. 3B is a schematic illustration of the radial valve configuration inFIG. 3A.

FIG. 4 is a schematic illustration of the collinear valve configurationin FIG. 1A.

FIG. 5 is a schematic representation of an exemplary main-stage manifoldemploying multiple main-stage valves arranged in a split collinearconfiguration.

FIG. 6A is an illustration of an exemplary main-stage manifold employingmultiple main-stage valves arranged in an annular configuration.

FIG. 6B is a schematic illustration of the annular valve configurationin FIG. 6A.

FIG. 7A is an exemplary main-stage manifold employing multiplemain-stage valves arranged in a 2×2 co-axial configuration.

FIG. 7B is a schematic illustration of the co-axial valve configurationin FIG. 7A.

FIG. 8 is a schematic representation of a valve assembly having a pilotvalve arranged externally along a longitudinal side of the main-stagevalve.

FIG. 9 is a schematic representation of a valve assembly having a pilotvalve arranged externally adjacent an end of the main-stage valve.

FIG. 10 is a schematic representation of a valve assembly having a pilotvalve arranged internally to the main-stage valve.

FIG. 11 is a schematic representation of an exemplary hydraulic systemincluding multiple main-stage valves, each employing a pilot valve foropening the main-stage valve and a return spring for closing themain-stage valve.

FIG. 12 is a schematic representation of an exemplary hydraulic systemincluding multiple main-stage valves, each employing a pilot valve foropening the main-stage valve and a shared return pressure valve forclosing the main-stage valves.

FIG. 13 is a schematic representation of an exemplary hydraulic systemincluding multiple main-stage valves, each employing a pilot valve foropening the main-stage valve and a pilot valve for closing themain-stage valve.

FIG. 14 is a schematic representation of an exemplary hydraulic systemincluding multiple main-stage valves employing multiple pilot valves foropening and closing the main-stage valves.

FIG. 15 provides a logic table identifying various options forcontrolling the operation of the main-stage valves employed with theexemplary hydraulic system of FIG. 14.

FIG. 16 is a schematic representation of the exemplary hydraulic systemof FIG. 14 employing a biasing member for preloading the main-stagespool to a closed position.

FIG. 17 provides a logic table identifying various options forcontrolling the operation of the main-stage valves employed with theexemplary hydraulic system of FIG. 16.

FIGS. 18 a and 18 b provide a logic table identifying various additionaloptions for controlling the operation of the main-stage valves employedwith the exemplary hydraulic system of FIG. 16.

FIG. 19A is a cross-sectional view of an exemplary main-stage valveemploying an integrated pressure assist mechanism configured to open themain-stage valve in response to an upstream pressure.

FIG. 19B is an enlarged view of a portion of the main-stage valve inFIG. 19A, shown arranged in a closed position.

FIG. 19C is a view of the portion of the main-stage valve shown in FIG.19B arranged in an open position.

FIG. 20A is a cross-sectional view of an exemplary main-stage valveemploying an integrated pressure assist mechanism configured to closethe main-stage valve in response to an upstream pressure.

FIG. 20B is an enlarged view of a portion of the main-stage valve shownin FIG. 20A arranged in a closed position.

FIG. 20C is a view of the portion of the main-stage valve shown in FIG.20B arranged in an open position.

FIG. 21A is a cross-sectional view of an exemplary main-stage valveemploying an integrated pressure assist mechanism configured to open themain-stage valve in response to a downstream pressure.

FIG. 21B is an enlarged view of a portion of the main-stage valve inFIG. 21A arranged in a closed position.

FIG. 21C is a view of the portion of the main-stage valve shown in FIG.21B arranged in an open position.

FIG. 22A is a cross-sectional view of an exemplary main-stage valveemploying an integrated pressure assist mechanism configured to closethe main-stage valve in response to a downstream pressure.

FIG. 22B is a view of a portion of the main-stage valve in FIG. 22Aarranged in a closed position.

FIG. 22C is a view of the portion of the main-stage valve shown in FIG.22B arranged in an open position.

FIG. 23 is a partial cross-sectional view of a damping system employedwith the main-stage valve for reducing impact forces occurring when aspool of the main-stage valve is moved between a closed position and anopen position.

FIG. 24 is an enlarged partial cross-sectional view of the dampingsystem in FIG. 23.

FIG. 25A is a partial cross-sectional view of a damping system employedwith a main-stage valve for reducing impact forces occurring when thespool of the main-stage valve is moved to the closed position.

FIG. 25B is an exploded view of a damping ring and a spool as seen inFIG. 25A.

FIG. 26 is a partial cross-sectional view of the co-linear valvearrangement of FIGS. 1A and 4 integrated with a hydraulic pump assembly.

FIG. 27 is a partial cross-sectional view of the split co-linear valvearrangement of FIG. 5 integrated with a hydraulic pump assembly.

FIG. 28A is a partial cross-sectional view of an exemplary main-stagemanifold employing multiple main-stage valves sharing a common spool andsleeve, with the spool arranged in a first position.

FIG. 28B is a partial cross-sectional view of the exemplary main-stagemanifold in FIG. 28A, with the spool arranged in a second position

FIG. 29A is a partial cross-sectional view of an exemplary main-stagemanifold employing a spool actuation surface located adjacent an outerend surface of the spool.

FIG. 29B is a partial cross-sectional view of the exemplary main-stagemanifold as shown in FIG. 29A, employing a spool actuation surfacelocated adjacent an inner end surface of the spool.

FIG. 30 is a partial cross-sectional view of an exemplary main-stagemanifold employing a ring shaped valve actuator.

FIG. 31A is partial cross-sectional view of an exemplary main-stagemanifold employing a pin shaped valve actuator.

FIG. 31B is a partial cross-sectional end view of the main-stagemanifold shown in FIG. 31A.

FIG. 32 is a schematic representation of an integrated hydraulic fluiddistribution module for minimizing compressible fluid volume andimproving system operating efficiency.

DETAILED DESCRIPTION

Referring now to the discussion that follows and also to the drawings,illustrative approaches to the disclosed systems and methods are shownin detail. Although the drawings represent some possible approaches, thedrawings are not necessarily to scale and certain features may beexaggerated, removed, or partially sectioned to better illustrate andexplain the disclosed device. Further, the descriptions set forth hereinare not intended to be exhaustive or otherwise limit or restrict theclaims to the precise forms and configurations shown in the drawings anddisclosed in the following detailed description.

FIG. 1A illustrates an exemplary hydraulic manifold 20 for controllingthe distribution of a pressurized fluid to multiple hydraulic loadshaving variable flow and pressure requirements. For purposes ofdiscussion, the manifold 20 is shown to include four separate valvesidentified as main-stage valves 30, 32, 34 and 36, respectively.Although the manifold 20 is shown to include four valves 30, 32, 34 and36 the manifold 20 may include fewer or more valves depending on therequirements of the particular application. Each main-stage valve may befluidly connected to one or more hydraulic loads. By way of example, thehydraulic loads may include, but are not limited to, varioushydraulically actuated devices, such as a hydraulic cylinder and ahydraulic motor. The main-stage valves control the operation of thehydraulic loads by selectively adjusting the pressure and flow of fluidto the respective hydraulic loads.

The valves 30, 32, 34 and 36 may be appropriately configured to enablethe valves to be interconnected in various configurations to form amain-stage manifold. In the main-stage manifold configurationillustrated in FIG. 1A, the main-stage valves are stacked together in aco-linear fashion. The term “collinear” denotes that the individualvalve spools are generally arranged end-to-end in a linear fashion. Themain-stage valves may also be arranged in a variety of otherconfigurations, examples of which are described subsequently.

The exemplary main-stage manifold may include an inlet port 42 throughwhich the high pressure fluid enters the manifold 20. Four exit ports44, 46, 48 and 50—one for each of the four main-stage valves—may befluidly connected to a corresponding hydraulic load. The inlet port 42may be fluidly connected to a source of pressurized fluid, such as afixed displacement pump (not shown). A wide variety of pumpconfigurations may be utilized, including but not limited, gear pumps,vane pumps, axial piston pumps, and radial piston pumps. It shall beappreciated, however, that other devices capable of generating a flow ofpressurized fluid may also be utilized. Pressurized fluid received fromthe fluid source enters the manifold 20 through the inlet port 42 andexits the main-stage manifold through one or more of the exit ports 44,46, 48 and 50. The valves 30, 32, 34 and 36 selectively control the flowof pressurized fluid from the inlet port 42 to the respective exit ports44, 46, 48 and 50.

Each of the valves 30, 32, 34 and 36 may include a hydraulicallyactuated spool valve 40. Each of the valves 30, 32, 34 and 36 includes avalve body 38 and a spool valve 40 disposed within the valve body 38.Each of the spool valves 40 may include a generally cylindrical-shapedhollow sleeve, illustrated as sleeves 64, that are fixed relative to thevalve body 38, and a generally cylindrical-shaped spool, illustrated asspools 66, which are slideably disposed around the outside of the sleeve64. The spools 66 are free to move back and forth over a portion of thelength of the sleeve 64. Although the terms “spool” and “sleeve” arecommonly used to describe components of a spool valve, the terms are notalways used consistently to refer to the same components. Accordingly,throughout this application, the term “sleeve” shall refer to thestationary component and the term “spool” shall refer to the componentthat is moveable relative to the stationary component. Thus, withrespect to the presently described spool valve 40, since the innermember is fixed relative to the valve body 38, it shall be referred toas the “sleeve”, whereas the outer member, which is described as beingmoveable relative to the sleeve, shall be referred to as the “spool”.If, on the other hand, the outer member were fixed relative to the valvebody and the inner member were moveable relative to the outer member,the inner member would be referred to as the “spool” and the outermember would be referred to as the “sleeve”.

The sleeves 64 and the spools 66 each may include a series of orificesthat extend through the walls of the respective components, where eachof the spools 66 include a series of orifices 80 and the sleeves 64include a series of orifices 82. The orifices 80 and 82 are generallyarranged in a common pattern to enable the orifices 80 in the spool 66to be generally aligned with the orifices 82 in the sleeve 64 when thespool 66 is positioned in an open position relative to the sleeve 64, asshown in FIG. 1C. The valves 30, 32, 34 and 36 can be arranged in anopen position (for example, valve 36 as shown in FIG. 1C) by sliding thespool 66 axially relative to the sleeve 64 so as to align the orifices80 in the spool 66 with the orifices 82 in the sleeve 64. Such anarrangement allows pressurized fluid to pass through the spool valves 40to the exit ports 44, 46, 48 and 50 of the valves 30, 32, 34 and 36,respectively. The spool 66 can be returned to a closed position (forexample, valve 36 as seen in FIG. 1A) by sliding the spool 66 axiallyrelative to the sleeve 64 so as to intentionally misalign the orificesin the spool 66 and the sleeve 64 to block the flow of fluid through thevalve. The spools 66 of each of the four valves 30, 32, 34 and 36 aredepicted in FIG. 1A in the closed position.

The valves 30, 32, 34 and 36 may be hydraulically actuated such as byway of a solenoid operated pilot valve 62. The pilot valve 62 mayinclude an inlet port 92 fluidly connected to a pressure source. Turningto FIG. 1B, an outlet port 96 of the pilot valve 62 may be fluidlyconnected to a fluid cavity 98 at least partially defined by a notchedregion 100 in the spool 66 and a wall 102 of the valve body 38. Thenotched region 100 of each spool 66 includes a generally verticallyoriented surface 108. Pressurizing the fluid cavity 98 exerts agenerally axial force against the surface 108 of the spool 66, whichtends to displace the spool 66 axially relative to the sleeve 64 to theopen position.

Turning back to FIG. 1A, the spool valves may each employ a biasingmember 106, which may include a variety of configurations, such as acoil spring and a leaf spring, for moving the spool 66 from the openposition to the closed position. The spool valve may also be configuredto have the biasing member move the spool 66 from the closed position tothe open position. The biasing member 106 exerts a biasing force againstthe spool 66 that may be generally opposite the biasing force producedby pressurizing the fluid cavity 98 at the opposite end of the spool 66.The valves 30, 32, 34 and 36 can be positioned in the open position bysufficiently pressurizing the fluid cavity 98 to overcome the biasingforce produced by the biasing member 106. Doing so causes the spool 66to slide axially relative to the sleeve 64 so as to fluidly connect theorifices 80 of the spool 66 with the orifices 82 of the sleeve 64, asshown in FIG. 1C. The positioning of the spool 66 relative to the sleeve64 may be controlled by means of a stop 110 that engages a first end 112of the spool 66, or another suitable region of the spool 66, when theorifices 80 in the spool 66 are fluidly connected to the orifices 82 inthe sleeve 64. Other mechanisms may also be employed for controlling thepositioning of the sleeve 64 relative to the spool 66.

The spool 66 may be positioned in the closed position by adjusting thepilot valve 62, so as to depressurize the fluid cavity 98. This allowsthe biasing force exerted by the biasing member 106 to slide the spool66 axially to the closed position. The orifices 80 in the spool 66 areintentionally axially misaligned with the orifices 82 in the sleeve 64when the spool 66 is positioned in the closed position. The positioningof the spool 66 in the closed position may be controlled by having anend 113 of the spool 66, or another suitable region of the spool 66,engage a second stop 114 positioned opposite the stop 110.

The valves 30, 32, 34 and 36 may be configured such that either theinner or outer member operates as the spool 66. In the exemplarymain-stage valve illustrated in FIG. 1A, the inner member functions asthe sleeve 64 and the outer member functions as the spool 66 (i.e., ismovable relative to the sleeve). As an alternative illustration,however, the inner member may be configured to operate as the spool 66and the outer member as the sleeve 64. Further, the valves 30, 32, 34and 36 may also be configured such that both the inner and outer membersmove simultaneously move in opposite directions relative to one anotherand the valve body 38. This latter configuration may produce fastervalve actuation speeds, but may also result in systems that are morecomplex.

Although the flow of pressurized fluid is described as passing radiallyoutward through the exemplary valves 30, 32, 34 and 36 when in the openposition, it shall be appreciated that the main-stage manifold may alsobe configured such that the flow passes radially inward. In that case,the passages designated as the respective exit ports 44, 46, 48 and 50in FIG. 1A would operate as an inlet port, and the passage designated asthe inlet port 42 would operate as an exit port. The direction in whichthe pressurized fluid passes through the valves 30, 32, 34 and 36 is notdependent on whether the inner or outer valve member operates as thespool, or whether both members are moveable relative to one another whenthe valves are actuated.

The valves 30, 32, 34 and 36, and the pilot valve 62 may have separatepressure supplies or may share a common pressure source. In theexemplary manifold configuration illustrated in FIG. 1A, the valves 30,32, 34 and 36, and the pilot valve 62, are shown sharing a commonpressure source. The pressurized fluid for supplying both the valves 30,32, 34 and 36, and the pilot valve 62, enters the main-stage manifoldthrough the inlet port 42. The inlet port 42 is fluidly connected to thesleeve 64 of the first valve 30.

The sleeves 64 of the valves 30, 32, 34 and 36 may be connected inseries to form an elongated plenum 120. Fluidly connected to adownstream end of the sleeve 64 of the last valve 36 in the series is apilot manifold 122. The pilot manifold 122 includes a pilot supplypassage 124 through which a portion of pressurized fluid may be bledfrom the main-stage fluid supply and delivered to the pilot valves 62.The inlet port 92 of each of the pilot valves 62 may be fluidlyconnected to the pilot supply passage 124. Upon actuating at least oneof the pilot valves 62, a portion of fluid present in the pilot supplypassages 124 passes through the pilot valve 62 to the fluid cavity 98adjoining the spool 66, thereby actuating at least one of the valves 30,32, 34 and 36 to the open position.

Continuing to refer to FIG. 1A, the pilot manifold 122 may include acheck valve 130. The check valve 130 operates to control the flow ofpressurized fluid delivered to the pilot manifold 122, and also toprevent fluid from back flowing from the pilot manifold 122 to plenum120. The check valve 130 may have any of a variety of configurations. Anexample of one such configuration is illustrated in FIG. 1A, where aball check valve is utilized to control the flow of fluid to and fromthe pilot manifold 122. The check valve 130 includes a ball 132 thatselectively engages an inlet passage 134 of the pilot manifold 122. Aspring 136 may be provided for biasing the ball 132 into engagement withthe inlet passage 134 of the pilot manifold 122. When the pressure dropacross the check valve 130 exceeds the biasing force exerted by thespring 136, the ball 132 will disengage the inlet passage 134 of thepilot manifold 122 to allow pressurized fluid to flow from the plenum120 to the pilot manifold 122. The rate at which fluid flows from thehydraulic manifold 20 to the pilot manifold 122 is dependent on thepressure drop across the check valve 130. The greater the pressure drop,the higher the flow rate. In instances where the pressure drop acrossthe check valve 130 is less then the biasing force of the spring 136, orthe pressure within the pilot manifold 122 exceeds the pressure withinthe plenum 120, the check valve ball 132 will engage the inlet passage134 of the pilot manifold 122 to prevent flow from passing through thecheck valve 130 in either direction. The spring rate of the spring 136can be selected so as to prevent the check valve 130 from opening untila desired pressure drop across the check valve 134 is achieved.

The pilot manifold 122 may also employ a filter 140 to remove debrisfrom hydraulic fluid. The filter 140 may be deployed in the pilot supplypassage 124 connecting the pilot valves 62 to the manifold 20. A widevariety of filters 140 may be employed, including but not limited to, aband filter and a cartridge filter, as well as others. A band filter hasthe advantage of being cost effective, generally has a smaller packagingenvelope than a cartridge filter, and may potentially be able totolerate higher pressure drops. A cartridge filter, on the other hand,can be replaced if it becomes clogged and generally has a largerfiltering surface area than a band filter, but may also require a largerpackaging envelope.

The pilot manifold 122 may also include an accumulator 142 for storingpressurized fluid used to actuate the valves 30, 32, 34 and 36. Theaccumulator 142 may have any of a variety of configurations. Forexample, one version depicted in FIG. 1A may include a fluid reservoir144 for receiving and storing pressurized fluid. The reservoir 144 maybe fluidly connected to the pilot manifold 122. The accumulator 142 mayinclude a moveable piston 146 positioned within the reservoir 144. Thepositioning of the piston 146 within the reservoir 144 can be adjustedto selectively vary the volume of the reservoir 144. A biasing mechanism148, such as a coil spring, urges the piston 146 in a direction thattends to minimize the volume of the reservoir 144. The biasing mechanism148 exerts a biasing force that opposes the pressure force exerted bythe pressurized fluid present within the pilot manifold 122. If the twoopposing forces are unbalanced, the piston 146 will be displaced toeither increase or decrease the volume of the reservoir 144, therebyrestoring the balance between the two opposing forces. In at least somesituations, the pressure level within the reservoir 144 corresponds tothe pressure within the pilot manifold 122. If the pressure force withinthe reservoir 144 exceeds the opposing force generated by the biasingmechanism 148, the piston 146 will be displaced toward the biasingmechanism 148, thereby increasing the volume of the reservoir 144 andthe amount of fluid that can be stored in the accumulator 142. As thereservoir 144 continues to fill with fluid, the opposing force generatedby the biasing mechanism 148 will also increase to the point at whichthe biasing force and the opposing pressure force exerted from withinthe reservoir 144 are substantially equal. The volumetric capacity ofthe reservoir 144 will remain substantially constant when the twoopposing forces are at equilibrium. On the other hand, actuating one ormore of the pilot valves 62 will generally cause the pressure levelwithin the pilot manifold 122 to drop below the pressure level withinthe reservoir 144. This coupled with the fact that the pressure forcesacross the piston 146 then become unbalanced will cause fluid stored inthe reservoir 144 to be discharged to the pilot manifold 122 for use inactuating the valves 30, 32, 34 and 36.

The valves 30, 32, 34 and 36 may be arranged within the manifold 20 invarious configurations. Examples of various valve arrangements aredescribed below, including but not limited to a co-parallelconfiguration, as shown in FIGS. 2A and 2B; a radial configuration, asshown in FIGS. 3A and 3B; a collinear configuration, as shown in FIGS.1A and 4; a split collinear configuration, as shown in FIG. 5; anannular configuration, as shown in FIGS. 6A and 6B; and a two by two(2×2) co-axial configuration, as shown in FIGS. 7A and 7B. The figuresdepicting the various valve arrangements each include a cross-sectionalview of the manifold 20 depicting the arrangement of the main-stagevalve and one or more schematic illustrations of the manifold 20illustrating the manner in which the fluid passes through the main-stagemanifold and individual main-stage valves (except for the splitcollinear arrangement shown in FIG. 5). These are merely a few of thepossible valve arrangements; in practice other arrangements may also beemployed depending on the requirements of a particular application. Theexemplary valve arrangements are not intended to be in any way limiting,as other arrangements may also be utilized.

Referring to FIG. 2A, manifold 220 includes two or more valves 230arranged in a co-parallel configuration, wherein a longitudinal axis A-Aof the valves 230 are aligned substantially parallel to one another. Aspool 266 and a sleeve 264 of each valve 230 may be arranged such thatthe spool 266 (moveable member) is the outer member and the sleeve 264(stationary member) is the inner member. The valve 230 may also beconfigured such that the outer member operates as the sleeve 264 and theinner member operates as the spool 266. The path of travel of the spool266 of each of the valves 230, which generally coincides with alongitudinal axis of the valve, may be aligned substantially parallel toone another. The path of travel between the spools 266 may liesubstantially within a common plane. The valves 230 may be arranged on acommon side of a manifold supply passage 222.

Turning also to FIG. 2B, an inlet 292 of each valve 230 may be fluidlyconnected to the manifold supply passage 222. Pressurized fluid entersthe manifold supply passage 222 through an inlet 242 fluidly connectedto a pressure source. The fluid passes through the manifold supplypassage 222 to the inlet 292 of the respective valves 230. Actuating(i.e., opening) one or more of the valves 230 allows pressurized fluidto pass from the manifold supply passage 222 to an inner cavity 232 ofthe spool 266 of the valve 230. From that point the fluid passesradially outwardly through orifices 280 in the sleeve 264 and orifices282 in the spool 266, and may be subsequently directed through acorresponding hydraulic circuit to a hydraulic load. In addition toproviding certain performance benefits, the co-parallel valvearrangement may also reduce manufacturing costs by simplifying machiningand assembly operations. This particular arrangement also enables themanifold 220 to be readily modified to include any number of valvesdepending on the requirements of the particular application.

Referring to FIGS. 3A and 3B, a manifold 320 may include two or morevalves 330 arranged in a radial configuration, where the valves 330 maybe arranged in a generally circular pattern around an axis A-A of acommon fluid node 342. The manifold 320 may include a series of supplypassages 391 that extend radially outwardly from the common fluid node342 in a manner resembling the spokes of a wheel, for example, as shownin FIG. 3B. An inlet port 392 of the valves 330 are fluidly connected toa supply passage 391. A spool 366 and a sleeve 364 of each valve 330 maybe arranged such that the spool 366 (moveable member) is the outermember and the sleeve 364 (stationary member) is the inner member,although the valve 330 may be configured such that the functions arereversed. Pressurized fluid may enter the supply passage 391 through aninlet port 393 that may be fluidly connected to a pressure source. Fluidpasses through the supply passage 391 to the inlet passages of therespective valves 330. Actuating (i.e., opening) one or more of thevalves 330 allows pressurized fluid to pass radially outward through theorifices 380 in the sleeve 364 and the orifices 382 in the spool 366,and subsequently through a corresponding hydraulic circuit to ahydraulic load.

Referring to FIGS. 1A and 4, the valves 30, 32, 34, 36 are shownarranged in a collinear configuration in the manifold 20, wherein thesleeves 64 of the valves 30, 32, 34, 36 are arranged end-to-end along acommon longitudinal axis A-A. FIG. 4 is a schematic illustration of themanifold of FIG. 1A, showing the fluid path through the manifold. Thespool 66 and the sleeve 64 of each valve 30, 32, 34, 36 are arrangedsuch that the spool 66 (moveable member) is the outer member and thesleeve 64 (stationary member) is the inner member. In this configurationthe sleeves 64 are connected together along the common longitudinal axisA-A to form a continuous cylindrical supply passage 91. Pressurizedfluid enters the supply passage through the inlet port 42 fluidlyconnected to a pressure source. Actuating (i.e., opening) one or more ofthe valves 30, 32, 34, 36 allows pressurized fluid to pass radiallyoutward through the orifices 80 in the spool 66 and the orifices 82 inthe sleeve 64 to an interconnected hydraulic circuit for supplying ahydraulic load. Fluid delivered to a particular valve passes through thesleeve 64 of each of the preceding valves prior to being delivered tothe particular valve. For example, fluid delivered to the last valve 36in the series passes through the sleeve 64 of each of the precedingvalves 30, 32 and 34. The collinear valve arrangement minimizes themain-stage inlet volume, which in turn may improve the overall operatingefficiency of the hydraulic system. The path of travel of the spool 66of each of the valves 30 may be aligned substantially parallel to oneanother, wherein the path of travel between the spools 66 may extendsubstantially along a common axis. The valves 30, 32, 34 and 36 may eachhave a common longitudinal axis A-A that may be arranged substantiallyparallel to the path of travel of the spools 66. The longitudinal axisA-A may be a common axis shared by all the valves 30, 32, 34 and 36, inthe manifold 20. The supply passage 91 may substantially coincide withthe axis A-A of the valves.

The exemplary valve arrangement depicted in FIG. 5 is a schematic viewof a modified version of the collinear valve arrangement illustrated inFIG. 4 that includes a manifold 520. This arrangement, referred to as asplit co-linear configuration, may include four valves 530 separatedinto two pairs arranged on opposite sides of a supply passage 592. Eachpair of valves 530 are arranged end-to-end in the manner described abovewith respect to the co-linear arrangement. Pressurized fluid is suppliedto each pair of valves 530 through the supply passage 592. Thepressurized fluid may pass through each pair of valves 530 as previouslydescribed with respect to the collinear valve arrangement, as shown inFIGS. 1A and 4. It shall be appreciated that each set of valves 530 mayinclude fewer or more than two valves 530. The path of travel of thespool of each of the valves 530 may be aligned substantially parallel toone another. The path of travel of the spools may substantially extendalong a common axis. For example, the valves 530 may be arranged along acommon longitudinal axis A-A that extends substantially parallel to thepath of travel of the spools, such that the longitudinal axis A-A is acommon axis shared by all the valves 530 in the manifold 520.

Referring to FIGS. 6A and 6B, a manifold 620 may include two or morevalves 630 arranged in an annular configuration similar to thearrangement shown in FIGS. 3A and 3B. The valves 630 may be arranged ina generally circular pattern around an axis A-A of an annular plenum693. The main-stage manifold 620 includes an inlet port 692 that may befluidly connected to a pressure supply. The inlet port 692 deliverspressurized fluid to the annular plenum 693. The valves 630 are arrangedaround and fluidly connected to the annular plenum 693. The spool 666and sleeve 664 of each valve 630 are arranged such that the spool 666(moveable member) is the outer member and the sleeve 664 (stationarymember) is the inner member. It shall be appreciated, however, that thevalve 630 may also be configured such that the outer member operates asthe sleeve 664 and the inner member operates as the spool 666.Pressurized fluid enters the inlet port 692 connected to a pressuresource. The fluid passes through the inlet port 692 to the annularplenum 693. Upon actuating (i.e., opening) one or more of the valves 630the pressurized fluid flows from the annular plenum 693 through thevalves 630 to an exit port 644. In contrast to the previously describedvalve arrangements, the pressurized fluid passes radially inward throughthe orifices in the spool 666 and the sleeve 664 to the interior of thesleeve 664. The interior of the sleeve 664 may be fluidly connected tothe exit port 644 of the valve 630. The exit ports 644 may be fluidlyconnected to a hydraulic load.

Referring to FIGS. 7A and 7B, a manifold 720 may include multiple valves730 arranged in a two by two (2×2) co-axial arrangement similar to thearrangement depicted in FIGS. 2A and 2B. This configuration may includetwo sets of valves 730 arranged on opposite sides of a common manifoldsupply passage 793. A longitudinal axis A-A of the valves 730 of a givenset are aligned generally parallel to one another. A spool 766 andsleeve 764 of each valve 730 are arranged such that the spool 766(moveable member) is the inner member and the sleeve 764 (stationarymember) is the outer member. It shall be appreciated, however, that thevalve 730 may also be configured such that the inner member operates asthe sleeve 764 and the outer member operates as the spool 766. An inlet791 of each valve 730 is fluidly connected to the manifold supplypassage 793. Pressurized fluid enters the manifold supply passage 793through an inlet port 792 fluidly connected to a pressure source. Thefluid passes through the manifold supply passage 793 to the inletpassage 791 of the respective valves 730. Actuating (i.e., opening) oneor more of the valves 730 allows pressurized fluid to pass from themanifold supply passage 793 to an inner cavity 732 of the spool 766.From that point the fluid passes radially outward through the orifices780 in the spool 766 and the orifices 782 in the sleeve 764 and may besubsequently directed through a corresponding hydraulic circuit to ahydraulic load. The path of travel of the spool 766 of each of thevalves 730 may be aligned substantially parallel to at least one othervalve 730 and may lie substantially within a common plane with at leastone other valve 730. Each of the valves 730 may share a commonlongitudinal axis A-A with at least one other valve 730.

Various options exist for mounting the pilot valve to the main-stagevalve. Three exemplary pilot valve mounting options are schematicallydepicted in FIGS. 8-10. For example, the pilot valve 862 may be mountedexternally to a side of the associated main-stage valve 830, as shown inFIG. 8. This arrangement is similar to the main-stage valve and pilotvalve arrangement shown in FIG. 1. The pilot valve 962 may also bemounted externally to an end of the main-stage valve 930, as shown inFIG. 9. The pilot valve 1062 may also be at least partially integratedinternally within the main-stage valve 1030, as shown in FIG. 10.

The valve arrangements illustrated in FIGS. 1A-10, may employ variousactuating schemes. An example of one such arrangement for actuating thevalves is illustrated schematically in FIG. 11. This arrangementutilizes a pilot valve 1162 and a biasing member, such as return spring1106, for controlling the actuation of each main-stage valve 1130.Return spring 1106 may have any of a variety of configurations,including but not limited to, a coil spring and a leaf spring. Separatepressure sources, such as pumps 1133 and 1135, may be provided forsupplying a flow of pressurized fluid to the pilot valve 1162 and themain-stage valves 1130, respectively. A pressure regulator may beprovided to control a discharge pressure of the pressure sources. Itshall be appreciated, however, that the pilot valves 1162 and themain-stage valves 1130 may also utilize a common pressure source. Anexample of an integrated pilot valve 1162 and main-stage valve manifoldconfigured to utilize a common pressure source is illustrated in FIGS.1A, 2A, and 3A.

Continuing to refer to FIG. 11, operation of the main-stage valve may becontrolled by the pilot valve 1162 and the return spring 1106. In oneexample, the pilot valve 1162 may be actuated by one or more solenoids.The solenoids may include a coil, which when energized moves the pilotvalve 1162 between an open position and a dump position. Arranging thepilot valve 1162 in the open position allows pressurized fluid from thepump 1133 to flow through the pilot valve 1162 to the main-stage valve1130. The pressurized fluid from the pilot valve 1162 causes the spoolof the main-stage valve 1130 to move to the open position (such aspreviously described with respect to FIG. 1A), thereby allowingpressurized fluid to flow from the pump 1135 through the valve 1130 to ahydraulic load 1137. Arranging the pilot valve 1162 in the dump positioncauses the pilot valve to stop the flow of pressurized fluid used toopen the valve 1130 and fluidly connects the pilot valve to a lowpressure reservoir 1163. This allows the biasing force of the returnspring 1106 to move the spool of the main-stage valve 1130 back to theclosed position, thereby blocking the flow of pressurized fluid to thehydraulic load 1137.

Utilizing a return spring 1106 to return the main-stage spool to theclosed position has the advantage of providing a failsafe mechanism inthe event there is a drop in system pressure. If that occurs, the returnspring 1106 will operate to close the valve 1130.

The return spring 1106 can be sized to achieve a desired balance betweenthe main-stage valve opening and closing response times. Increasing ordecreasing the spring rate of the return spring 1106 may affect theopening and closing response times differently. For example, increasingthe spring rate will generally result in a corresponding decrease in theclosing response time and a corresponding increase in the openingresponse time for a given supply pressure. The corresponding increase inthe opening response time is due to the fact that the biasing force ofthe return spring 1106 tends to resist the motion of the pilotcontrolled actuation force. The corresponding increase in openingresponse time may be overcome, for instance, by increasing the pressureused to activate the main-stage valve 1130, although doing so may notalways be a viable alternative. Conversely, decreasing the spring rateof the return spring 1106 will generally result in a correspondingincrease in the closing response time and a corresponding decrease inthe opening response time. Accordingly, the sizing of the return spring1106 may depend on various factors, including but not limited to themagnitude of the pilot controlled actuation force as well as the desiredvalve opening and closing response times required for a particularapplication.

With reference to FIG. 12, the main-stage valve actuating schemeillustrated in FIG. 11 may be modified by eliminating the main-stagereturn springs 1106, and instead using hydraulic pressure to close themain-stage valves 1230. The return pressure used to close the main-stagevalves 1230 may be controlled by way of a single return pressure valve1232. This arrangement utilizes a common pressure source, illustrated aspump 1233. A pressure regulator may be provided to control a dischargepressure of the pressure sources. The pump 1233 may be used to supplythe necessary pressure for opening and closing the main-stage valves1230. The closing response time for this configuration is generallyproportional to the pressure output of the return pressure valve 1232.Increasing the output pressure of the return pressure valve 1232 willgenerally produce a corresponding decrease in the valve 1230 closingresponse time, whereas decreasing the output pressure will generallyresult in a corresponding increase in the response time. The returnpressure valve 1232 may be configured to produce a minimum outputpressure greater than the pressure required to drain the fluid from thepilot valves 1262 so as to provide sufficient pressure to move the spoolof the main-stage valve 1230 to the closed position within a desiredresponse time. A pressure regulator 1240 may be provided for controllingthe pressure supplied to the main-stage valve 1230 from pilot valve1232. The pressure regulator controls the pressure discharged from pilotvalve 1232 by selectively fluidly connecting a discharge port 1242 ofpilot valve 1232 to a low pressure reservoir 1263. The pressureregulator allows at least a portion of the pressurized fluid dischargedfrom the pilot valve 1232 to be directed back to the reservoir 1263 whenthe pilot valve discharge pressure exceeds a predetermined pressure.Separate pressure sources, such as pumps 1233 and 1235, may be providedfor supplying a flow of pressurized fluid to the pilot valve 1262 andthe main-stage valves 1230, respectively. The pilot valves 1262 and themain-stage valves 1230 may also utilize a common pressure source, suchas illustrated in FIGS. 1A, 2A, and 3A.

Operation of the main-stage valves 1230 are controlled by the pilotvalves 1262 and the single return pressure valve 1232. In one example,the pilot valve 1262 may be actuated by one or more solenoids. Eachsolenoid may include a coil, which when energized urges the pilot valve1262 to move between an open position and a closed position. Whenarranged in the open position, the pilot valve 1262 allows pressurizedfluid from the pump 1233 to flow through the pilot valve 1262 to themain-stage valve 1230. The pressurized fluid from the pilot valve 1262causes a spool of the main-stage valve 1230 to move to the open position(for example, in the manner described with respect to FIG. 1A), therebyallowing pressurized fluid to flow from the pump 1235 through themain-stage valve 1230 to a hydraulic load 1237. Arranging the pilotvalve 1262 in the closed position stops the flow of pressurized fluidused to open the main-stage valve 1230. The single return pressure valve1232 may be used to control the pressure needed to move the spool of themain-stage valve 1230 back to the closed position, thereby blocking theflow of pressurized fluid to the hydraulic load 1237.

Continuing to refer to FIG. 12, although this arrangement does notutilize a return spring to move the main-stage spool to the closedposition, a return spring may nevertheless be employed to provide afailsafe mechanism for closing the main-stage valves 1230 in the eventof a loss or drop in system pressure. Since the return spring is notbeing utilized as the primary means for returning the main-stage spoolto the closed position, the spring rate of the return spring can besignificantly lower than may otherwise be required if a pressure sourcewere not applying pressure to close the main-stage valves 1230.

FIG. 13 illustrates a main-stage valve control scheme similar to thatshown in FIG. 12. As is the case with the configuration shown in FIG.12, hydraulic pressure, rather than a return spring, is used to closethe main-stage valves 1330. But in contrast to the configuration shownin FIG. 12, this configuration utilizes separate pilot valves 1332,rather than a single return pressure valve (i.e., valve 1232 in FIG.12), to control the pressure delivered to the main-stage valves 1330 forclosing the valves. Each main-stage valve 1330 may thus employ twoseparate pilot valves 1332 and 1362. The pilot valve 1362 controls theopening of the main-stage valve 1330 and the other pilot valve 1332controls the closing of the main-stage valve 1330. Although thisarrangement does not utilize a return spring to move the main-stagespool to the closed position, a return spring may nevertheless beemployed to provide a failsafe mechanism for closing the main-stagevalve 1330 in the event of a loss or drop in system pressure. Since thereturn spring is not being utilized as the primary means for returningthe main-stage spool to the closed position, the spring rate of thereturn spring can be significantly lower than may otherwise be requiredif a pressure source were not applying pressure to close the main-stagevalve 1330. Separate pressure sources, such as pumps 1333 and 1335, maybe provided for supplying a flow of pressurized fluid to the pilotvalves 1332 and 1362, as well as the valves 1330, respectively. Apressure regulator may be provided to control a discharge pressure ofthe pressure sources. It shall be appreciated, however, that the pilotvalves 1332 and 1362 as well as the main-stage valves 1330 may alsoutilize a common pressure source, as illustrated in FIGS. 1A, 2A, and3A.

Operation of the main-stage valve 1330 is controlled by the pilot valves1332 and 1362. In one example, the pilot valves 1332 and 1362 may beactuated by one or more solenoids. The solenoids may include a coil,which when energized urges the pilot valves 1332 and 1362 to movebetween an open position and a dump position. When arranged in the openposition, the pilot valve 1362 allows pressurized fluid from the pump1333 to flow through the pilot valve 1362 to the main-stage valve 1330.The pressurized fluid from the pilot valve 1362 causes a spool of themain-stage valve 1330 to move to the open position, thereby allowingpressurized fluid to flow from the pump 1335 through the main-stagevalve 1330 to a hydraulic load 1337. Arranging the pilot valve 1362 inthe dump position stops the flow of pressurized fluid used to open themain-stage valve 1330 and fluidly connects the pilot valve 1362 with areservoir 1363. With pilot valve 1362 arranged in the dump position, thepilot valve 1332 may then be opened to supply the pressure needed tomove the spool of the main-stage valve 1330 back to the closed position,thereby blocking the flow of pressurized fluid to the hydraulic load1337.

FIG. 14 schematically illustrates a main-stage valve actuating schemethat takes advantage of the combined actuating areas of adjacentmain-stage valve spools 1430 to minimize the number of pilot valves 1462that may be required to open and close the main-stage valves 1430.Separate pressure sources, such as pumps 1433 and 1435, may be providedfor supplying a flow of pressurized fluid to the pilot valves 1462 andthe main-stage valves 1430, respectively. A pressure regulator may beprovided to control a discharge pressure of the pressure sources. Itshall be appreciated, however, that the pilot valves 1462, as well asthe main-stage valves 1430, may also utilize a common pressure source,such as illustrated in FIGS. 1A, 2A, and 3A, for example. Eachmain-stage valve 1430 may employ two separate pilot valves 1462. Onepilot valve 1462 operates to open the main-stage valve 1430 and theother pilot valve 1462 operates to close the main-stage valve 1430. Themain-stage valves 1430 located at the ends of the valve series share apilot valve 1462 with the adjacent main-stage valve 1430. For example,main-stage valve (1) (the four main-stage valves 1430 in FIG. 14 areindividually identified as valves (1)-(4)) will share pilot valve B (thefive pilot valves 1462 in FIG. 14 are individually identified as valvesA-E) with adjacent main-stage valve (2), and main-stage valve (4) willshare pilot valve D with adjacent main-stage valve (3). The valves 1430located in the middle of the valve series will share two pilot valves1462. For example, main-stage valve (2) shares pilot valve B withadjacent main-stage valve (1) and pilot valve C with adjacent main-stagevalve (3).

The pilot valves 1462 may be actuated by one or more solenoids. Thesolenoids may include a coil, which when energized may urge the pilotvalve 1462 to move between an open position and a dump position. Whenplaced in the open position, the pilot valve 1462 allows pressurizedfluid from a pump 1433 to flow through the pilot valve 1462 to themain-stage valve 1430. Arranging the pilot valve 1462 in the dumpposition fluidly connects the pilot valve to a low pressure reservoir1463. Shared pilot valves 1462 may operate to simultaneously apply anopening pressure to one of the shared valves 1430 and closing pressureto the other of the shared valves 1430. For example, arranging the pilotvalve B in the open position allows pressurized fluid from a pump 1433to flow through the pilot valve B to the main-stage valve (2). With thepilot valves A and C arranged in the dump position, the pressurizedfluid from the pilot valve B causes the spool of the main-stage valve(2) to move to the open position, thereby allowing pressurized fluid toflow from the pump 1433 through the main-stage valve (2) to a hydraulicload 1437. Arranging the pilot valve B in the open positionsimultaneously applies a closing pressure to the main-stage valve (1).The main-stage valves may also be configured such that the shared pilotvalves 1462 operate to simultaneously apply an opening pressure to bothshared main-stage valves 1430 or a closing pressure to both sharedmain-stage valves 1430. For example, opening pilot valve B maysimultaneously apply a closing pressure to both main-stage valve (1) andmain-stage valve (2). This arrangement may minimize the number of pilotvalves 1462 by using a single pilot valve 1462 to control the operationof two main-stage valves 1430.

A logic table identifying various control schemes for opening andclosing each of the main-stage valves 1430 of FIG. 14 is provided inTable 1 of FIG. 15. The table describes the effect that various pilotvalve operating conditions have on the operation of the correspondingmain-stage valve. For example, opening pilot valve A to pressure (valveposition “1”) will open main-stage valve (1) (valve position “1”). Thiswill not have an effect on the position of the remaining threemain-stage valves, which will maintain their previous positions (valveposition “LC”), provided that the remaining pilot valves are opened todrain (valve position “0”). Opening pilot valve B (valve position “1”),which is shared by main-stage valves (1) and (2), and opening pilotvalve A to drain (valve position “0”) will result in main-stage valve(1) closing (valve position “0”) and main-stage valve (2) opening (valveposition “1”). Main-stage valves 3 and 4 will maintain their previouspositions (valve position “LC”) provided that the associated pilotvalves are open to drain. The effect that opening the other pilot valves(i.e., pilot valves C, D and E) has on the operation of the main-stagevalves can be readily determined from Table 1 of FIG. 15.

FIG. 16 schematically illustrates a main-stage valve actuating schemesimilar to that shown in FIG. 14. A difference is the addition of abiasing member 1606 that operates to preload a spool of the main-stagevalve 1630 to a closed position. The biasing member 1606 also provides afailsafe mechanism for closing the main-stage valve 1630 in the event ofa loss or reduction in system pressure. The biasing member 1606 may alsominimize feedback effects due to pressure changes that may occur whenadjacent main-stage valves 1630 are actuated.

Separate pressure sources, such as pumps 1633 and 1635, may be providedfor supplying a flow of pressurized fluid to pilot valves 1662 andmain-stage valves 1630, respectively. A pressure regulator may beprovided to control a discharge pressure of the pressure sources. Thepilot valves 1662, as well as the main-stage valves 1630, may alsoutilize a common pressure source, such as illustrated in FIGS. 1A, 2A,and 3A, for example. Each main-stage valve 1630 (the four main-stagevalves are individually identified as valves (1)-(4) in FIG. 16) mayemploy two separate pilot valves 1662 (the five pilot valves areindividually identified as valve A-E in FIG. 16). One pilot valve 1662operates to open the main-stage valve 1630 and the other pilot valve1662 operates to close the main-stage valve 1630. The main-stage valves1630 located at the ends of the valve series will share a pilot valve1662 with the adjacent main-stage valve 1630. For example, main-stagevalve (1) will share pilot valve B with adjacent main-stage valve (2),and main-stage valve (4) will share pilot valve E with adjacentmain-stage valve (3). The main-stage valves 1630 located in the middleof the valve series will share two pilot valves 1662. For example,main-stage valve (2) shares pilot valve B with adjacent main-stage valve(1) and pilot valve C with adjacent main-stage valve (3).

The pilot valves 1662 may be actuated by one or more solenoids. Thesolenoids may include a coil, which when energized may urge the pilotvalve 1662 to move between an open position and a dump position. Whenplaced in the open position, the pilot valve 1662 allows pressurizedfluid from a pump 1633 to flow through the pilot valve 1662 to themain-stage valve 1630. Arranging the pilot valve 1662 in the dumpposition fluidly connects the pilot valve to a low pressure reservoir1663. Shared pilot valves 1662 operate to simultaneously apply anopening pressure to one of the shared main-stage valves 1630 and closingpressure to the other of the shared main-stage valves 1630. For example,arranging the pilot valve B in the open position allows pressurizedfluid from the pump 1633 to flow through the pilot valve B to themain-stage valve (2). With the pilot valves A and C arranged in the dumpposition, the pressurized fluid from the pilot valve B causes the spoolof the main-stage valve (2) to move to the open position, therebyallowing pressurized fluid to flow from the pump 1633 through themain-stage valve (2) to a hydraulic load 1637. Arranging the pilot valveB in the open position simultaneously applies a closing pressure tomain-stage valve (1). The biasing member 1606 provides a failsafemechanism for closing the main-stage valve 1630 in the event of a lossor reduction in system pressure. The main-stage valves may also beconfigured such that the shared pilot valves 1662 operate tosimultaneously apply an opening pressure to both shared main-stagevalves or a closing pressure to both shared main-stage valves 1662. Forexample, opening pilot valve B may simultaneously apply a closingpressure to both main-stage valve (1) and main-stage valve (2). Thisarrangement may minimize the number of pilot valves 1662 by using asingle pilot valve 1662 to control the operation of two main-stagevalves 1630.

Exemplary control logic for controlling the opening and closing of themain-stage valves 1630 employed in the control scheme shown in FIG. 16is provided in the Table 2 of FIG. 17. For example, if pilot valve A isopen to pressure (valve position “1” in Table 2) and pilot valves B-Eare open to drain (valve position “0” in Table 2), this will result inmain-stage valve (1) opening (valve position “1” in Table 2) and theremaining main-stage valves 1630 remaining closed (valve position “0” inTable 2). The effect of various other pilot valve operating sequencesmay be readily determined from Table 2 of FIG. 17.

Table 3 of FIGS. 18A and 18B describes exemplary control logic that maybe employed with the control scheme shown in FIG. 16. Unlike the controllogic provided in Table 2 of FIG. 17, wherein only one main-stage valveis opened at a given time, the control logic provided in Table 3 allowsmultiple main-stage valves to be opened simultaneously. The control datain Table 3 of FIGS. 18A and 18B may be interpreted in the same manner asthe control data in Table 2 of FIG. 17.

FIGS. 19A-22B illustrate various exemplary main-stage valveconfigurations employing an integrated pressure assist mechanism. Theintegrated pressure assist mechanism operates to urge the spool of themain-stage valve toward either an open position or a closed position,depending on the particular configuration of the pressure assistmechanism, in response to the presence of a predetermined upstream ordownstream pressure. For purposes of discussion, the outer memberoperates as the spool and the inner member operates as the sleeve, andthe “upstream pressure” (Pu) refers to the pressure occurring within aninterior of the sleeve and the “downstream pressure” (Pd) refers to thepressure in the region surrounding the outside of the spool.

FIG. 19A illustrates an exemplary pressure assist mechanism 1910configured to open a valve 1930 in response to a predetermined upstreampressure Pu. FIG. 20A illustrates an exemplary pressure assist mechanism2010 configured to close a valve 2030 in response to a predeterminedupstream pressure Pu. FIG. 21A illustrates an exemplary pressure assistmechanism 2110 configured to open a valve 2130 in response to apredetermined downstream pressure Pd. FIG. 22A illustrates an exemplarypressure assist mechanism 2210 configured to close a valve 2230 inresponse to a predetermined downstream pressure Pd.

The pressure assist mechanism may be incorporated into the main-stagevalve by providing a step 1911, 2011, 2111 and 2211 in the respectivepressure assist mechanisms 1910, 2010, 2110 and 2210. Each step consistsof a step 1912, 2012, 2112 and 2212 formed in a corresponding valvespool, 1966, 2066, 2166 and 2266, respectively, as indicated in FIGS.19A-22B. A corresponding step 1914, 2014, 2114 and 2214 is alsoincorporated into a sleeve 1964, 2064, 2164 and 2264, respectively. Thestep causes opposing pressure induced axial forces to be exerted againstthe spool and the sleeve, which tend to cause the valve to either openor close depending on the particular configuration of the pressureassist mechanism. The magnitude of the opposing forces is determined, atleast in part, by the size of the step. The larger the step the largerthe opposing forces for a given pressure drop.

Continuing to refer to FIGS. 19A-22B, the placement of the step relativeto orifices in the sleeve (i.e., orifices 1982, 2082, 2182 and 2282) andthe spool (i.e., orifices 1980, 2080, 2180 and 2280) determines whetherthe pressure assist mechanism is responsive to the upstream pressure Puor downstream pressure Pd. If the step occurs across an orifice of thesleeve when the valve is closed, such as the configuration shown inFIGS. 19A and 20A, the pressure assist mechanism will be responsive tothe upstream pressure Pu. If the step occurs across an orifice of thespool when the valve is closed, such as the configuration shown in FIGS.21A and 22A, the pressure assist mechanism will be responsive to thedownstream pressure Pd.

As can be observed from FIGS. 19A-22B, one side of the step may bedefined by the spool and an opposite side of the step may be defined bythe sleeve. The step in the spool and the sleeve at least partiallydefine a fluid pathway 1913, 2013, 2113 and 2213 between the orifice inthe spool and the corresponding orifice in the sleeve when the valve isopen. Whether the pressure assist mechanism operates to open or closethe valve is determined by which side of the orifice the spool portionof the step is positioned. Positioning the spool portion of the stepalongside an edge of the orifice nearest the return spring, such as theconfiguration shown in FIGS. 19A and 21A, will result in the pressureassist mechanism opening the main-stage valve when a predeterminedpressure is achieved. Positioning the spool portion of the stepalongside the opposite edge of the orifice away from the return spring,such as the configuration shown in FIGS. 20A and 22A, will result in thepressure assist mechanism closing the main-stage valve when apredetermined pressure is achieved.

Referring to FIGS. 19A thru 19C, the step 1911 of the pressure assistmechanism 1910 is positioned across the orifice 1982 of the sleeve 1964(stationary member) when the valve 1930 is arranged in the closedposition (i.e., FIGS. 19A and 19B), and consequently the pressure assistmechanism 1910 will be responsive to the upstream pressure Pu (i.e.,pressure occurring within the interior region of the sleeve 1964). FIG.19B is an enlarged view of the pressure assist mechanism 1910, showingthe step 1912 in the spool 1966, and the step 1914 in the sleeve 1964.The spool portion of the step 1912 is located alongside the orifice 1982nearest a return spring 1906. The return spring 1906 may be incommunication with at least the spool 1966, and operates to urge thespool 1966 toward the closed position (i.e., FIGS. 19A and 19B) from theopen position (i.e., FIG. 19C). Thus, the pressure occurring within theorifice 1982 of the sleeve 1964 will tend to push the step 1912 awayfrom the step 1914 of the sleeve 1964, and toward the return spring1906, thereby opening the valve 1930 when the predetermined pressure isachieved, such as illustrated in FIG. 19C.

The steps 1912 and 1914 cooperate with one another to at least partiallydefine the fluid pathway 1913 between the orifice 1982 of the sleeve1964 and the orifice 1980 of the spool 1966 when the valve 1930 isarranged in the open position, as shown in FIG. 19C. With the valve 1930arranged in the open position, the steps 1912 and 1914 may be fluidlyconnected to the orifices 1980 and 1982. The steps 1912 and 1914 may besubstantially fluidly disconnected from the orifice 1980 when the valve1930 is arranged in the closed position, as shown in FIGS. 19A and 19B,but remain fluidly connected to orifice 1982.

Referring to FIGS. 20A thru 20C, the step 2011 of the pressure assistmechanism 2010 is positioned across the orifice 2082 of the sleeve 2064(stationary member) when the valve 2030 is arranged in a closed position(i.e., FIGS. 20A and 20B), and consequently the pressure assistmechanism 2010 will be responsive to the upstream pressure Pu (i.e.,pressure occurring within the interior region of the sleeve 2064). Thespool portion 2066 of the step 2012 is located alongside the orifice2082 furthest from a return spring 2006. The return spring 2006 operatesto urge the spool 2066 toward the closed position (i.e., FIGS. 20A and20B) from the open position (i.e., FIG. 20C). FIG. 20B is an enlargedview of the pressure assist mechanism 2010, illustrating the positioningof the step 2012 in the spool 2066, as well as the corresponding step2014 in the sleeve 2064, when the valve 2030 is arranged in the closedposition. FIG. 20C is an enlarged view of the valve 2030 arranged in theopen position, with the orifices 2080 of the spool 2066 fluidlyconnected to the orifices 2082 of the sleeve 2064. The pressureoccurring within the orifice 2082 of the sleeve 2064 will tend to urgethe step 2012 of the spool 2066 away from the step 2014 of the sleeve2064 and away from the return spring 2006, thereby closing the valve2030 when a predetermined pressure is achieved, such as shown in FIGS.20A and 20B.

The steps 2012 and 2014 cooperate with one another to at least partiallydefine the fluid pathway 2013 between the orifice 2082 of the sleeve2064 and the orifice 2080 of the spool 2066 when the valve 2030 isarranged in the open position, as shown in FIG. 20C. When the valve 2030is arrange in the open position (FIG. 20C), the steps 2012 and 2014 maybe fluidly connected to the orifices 2080 and 2082. The steps 2012 and2014 may be substantially fluidly disconnected from the orifice 2080when the valve 2030 is arranged in the closed position, as seen in FIGS.20A and B, but remain fluidly connected to orifice 2082.

Referring to FIGS. 21A thru 21C, the step 2111 of the pressure assistmechanism 2110 is positioned across the orifice 2180 of the spool 2166(moveable member) when the spool 2166 is arranged in a closed position(i.e., FIGS. 21A and 21B), and as a consequence, the pressure assistmechanism 2010 will be responsive to the downstream pressure Pd (i.e.,pressure occurring around the exterior region of the spool 2166). Thespool portion of the step 2111 is located alongside the orifice 2180nearest a return spring 2106. The return spring 2106 operates to urgethe spool 2166 toward the closed position (i.e., FIGS. 21A and 21B).FIG. 21B is an enlarged view of the pressure assist mechanism 2110,showing the positioning of the step 2112 in the spool 2166, and thecorresponding step 2114 in the sleeve 2164, with the valve 2130 arrangedin the closed position, and FIG. 21C is an enlarged view of the valve2130 with the spool 2166 arranged in an open position. The pressureoccurring within the orifice 2180 of the spool 2166 will tend to pushthe step 2112 away from the step 2114 of the spool 2166 and toward thereturn spring 2106, thereby opening the valve 2130 when a predeterminedpressure is achieved, such as illustrated in FIG. 21C.

The steps 2112 and 2114 cooperate with one another to at least partiallydefine the fluid pathway 2113 between the orifice 2182 of the sleeve2164 and the orifice 2180 of the spool 2166 when the valve 2130 isarranged in the open position, as shown in FIG. 21C. With the valve 2130arranged in the open position, the steps 2112 and 2114 are fluidlyconnected to the orifices 2180 and 2182. The steps 2112 and 2114 may besubstantially fluidly disconnected from the orifice 2182 when the valve2130 is arranged in the closed position, as shown in FIGS. 21A and 21B,but remain fluidly connected to orifice 2180.

Referring to FIGS. 22A thru 22C, the step 2211 of the pressure assistmechanism 2210 is positioned across the orifice 2280 of the spool 2266(moveable member) when the spool is arranged in a closed position (i.e.,FIGS. 22A and 22B), and thus, the pressure assist mechanism 2210 will beresponsive to the downstream pressure Pd (i.e., pressure occurringaround the exterior region of the spool 2266). FIG. 22B is an enlargedview of the pressure assist mechanism 2210 showing the relativepositioning of the step 2212 in the spool 2266 and the step 2214 in thesleeve 2264 when the valve 2230 is arranged in a closed position, andFIG. 22C is an enlarged view of the valve 2230 with the spool 2266arranged in an open position. The spool portion of the step 2212 islocated alongside the orifice 2280 furthest from a return spring 2206.The return spring 2206 operates to urge the spool 2266 toward the closedposition, as shown in FIGS. 22A and 22B. Thus, the pressure occurringwithin the orifice 2280 of the spool 2266 will tend to push the step2212 away from the step 2214 of the spool 2266 and away from the returnspring 2206, thereby urging the valve 2230 toward the closed positionwhen a predetermined pressure is achieved.

The steps 2212 and 2214 cooperate with one another to at least partiallydefine the fluid pathway 2213 between the orifice 2282 of the sleeve2264 and the orifice 2280 of the spool 2266 when the valve 2230 isarranged in the open position, as shown in FIG. 22C. With the valve 2230in the open position, the steps 2212 and 2214 may be fluidly connectedto the orifices 2280 and 2282. The steps 2212 and 2214 may besubstantially fluidly disconnected from the orifice 2282 when the valve2230 is arranged in the closed position, as shown in FIGS. 22A and 22B,but remain fluidly connected to orifice 2280.

It should be noted that, although pressure assist mechanisms 1910, 2010,2110 and 2210 are illustrated as being positioned across the orificelocated either furthest or closest to the return spring, the step of thepressure assist mechanisms 1910, 2010, 2010 and 2210 may be locatedacross any of the orifices in the spool or the sleeve. Also, in anotherexample, the steps of the pressure assist mechanisms 1910, 2010, 2110and 2210 may be located at any position along the spool or the sleeve,provide the pressure assist mechanism is in fluid communication with anorifice of the sleeve or the spool.

Cycling the main-stage valve between the open and closed positions maygenerate high impact forces when the spool contacts stops that limit thetravel of the spool. This may not only produce undesirable noise, butmay also impact the durability of the main-stage valve and the accuracywith which the valve can be controlled. FIG. 23 is an illustration of anexemplary valve 2330 employing a spool 2366 having a damper 2312 fixedlyattached to an end of the spool. The damper 2312 may be constructed froman elastically compliant material for absorbing at least a portion ofthe impact forces occurring when the valve is moved from the openposition to the closed position. A generally opposing end of the valve2330 may include a second damper 2310 that operates to dampen the impactforces occurring when the valve is moved from the closed position to theopen position. FIG. 24 is an enlarged view of the end of the main-stagespool 2366, showing a stop region 2311 of the damper 2312 contacting astop 2320 of a valve housing 2319 when the valve is arranged in theclosed position.

The valve 2330 may include a generally cylindrical-shaped hollow sleeve2364 fixed relative to the valve housing 2319, and the generallycylindrical-shaped spool 2366, which is slideably disposed around theoutside of the sleeve 2364. The spool 2366 is free to move back andforth over a portion of the length of the sleeve 2364 between the openposition and the closed position. FIGS. 23 and 24 illustrate the valve2330 arranged in the closed position. The valve 2330 may employ abiasing member, which is illustrated as a return spring 2306, for movingthe spool 2366 from the open position to the closed position.

Referring to FIG. 23, the sleeve 2364 and the spool 2366 each mayinclude a series of orifices 2382 and 2380 that extend through the wallsof the respective components. The orifices 2380 in the spool 2366 arefluidly connected to the orifices 2382 in the sleeve 2364 when the spool2366 is positioned in an open position relative to the sleeve 2364. Theorifices 2380 and 2382 are substantially fluidly disconnected from theorifices 2382 in the sleeve 2364 when the spool 2366 is positioned in aclosed position relative to the sleeve 2364.

Continuing to refer to FIG. 23, the impact forces produced upon openingthe valve 2330 may be dampened by constructing the damper 2310 from anelastically compliant material. Suitable materials may include, but arenot limited to, engineered plastics, such as polyetheretherkeone havingapproximately twenty percent carbon fiber filler. The damper 2310 mayinclude a bearing surface 2308 that engages an end of the spool 2366.The damper 2310 may further include a stop region 2316 having an end2317 that engages the valve housing 2319 to limit the travel of themain-stage spool 2366 upon opening. Opening the valve 2330 causes thespool 2366 to displace the damper 2310 toward the housing 2319. Thedamper 2310 may elastically deform upon impacting the valve housing 2319to absorb at least a portion of the impact energy. The damper 2310 mayalso include a flange 2313 that engages an end of the biasing member2306. An opposite end of the biasing member engages the valve housing2319. At least a portion of damper 2310 may be disposed within thebiasing member 2306. The biasing member 2306 operates to urge the spool2366 toward the closed position. The end 2317 of the damper 2310 isdisengaged from the housing 2319 when the spool 2366 is displaced awayfrom the open position.

With reference to FIG. 24, the impact forces produced upon closing thevalve 2330 may be dampened by forming the damper 2312 from anelastically compliant material. The stop region 2311 of damper 2312 mayinclude a shoulder 2314 that engages the stop 2320 formed in the valvehousing 2319 as the spool 2366 of the valve 2330 is moved to the closedposition. The shoulder 2314 may be any surface of the damper 2312 thatcontacts the surface of the stop 2320 of the valve housing as the valve2330 is closed.

The damper 2312 may elastically deform to absorb at least a portion ofthe impact energy that is created as the shoulder 2314 of the dampercontacts the stop 2320 of the valve housing as the valve 2330 is closed.The shoulder 2314 disengages the stop 2320 when the valve 2330 is movedto the open position. Suitable materials for the damper 2312 mayinclude, but are not limited to, engineered plastics, such aspolyetheretherkeone having approximately twenty percent carbon fiberfiller. When the damper 2312 impacts the stop 2320 upon closing thevalve 2330, the elastically compliant material elastically deforms toabsorb at least a portion of the impact energy and cushion the impact.The elastically compliant material may be the same or a differentmaterial than the material used to construct the remaining portion ofthe spool 2366.

With reference to FIG. 25A, the impact forces produced upon closing avalve 2530 may be dampened by forming a portion of a spool 2566 thatcontacts the valve housing out of an elastically compliant materialcapable of absorbing at least a portion of the impact forces occurringwhen the valve is closes. The valve 2530 may include a generallycylindrical-shaped hollow sleeve 2564 fixed relative to a valve body1519, and the generally cylindrical-shaped spool 2566, which isslideably disposed around the outside of the sleeve 2564. The spool 2566is free to move back and forth over a portion of the length of thesleeve 2564 between an open position and a closed position. FIG. 25Aillustrates the valve 2530 arranged in the closed position. The sleeve2564 and the spool 2566 each may include a series of orifices 2582 and2580 that extend through the walls of the respective components. Theorifices 2580 and 2582 are generally arranged in a common pattern toenable the orifices 2580 in the spool 2566 to be generally aligned withthe orifices 2582 in the sleeve 2564 when the spool 2566 is positionedin the open position relative to the sleeve 2564. The orifices 2580 and2582 are generally misaligned with the orifices 2582 in the sleeve 2564when the spool 2566 is positioned in the closed position relative to thesleeve 2564

The spool 2566 may include a stepped region 2518 that engages a stop2510 formed in a valve housing 2519. The stepped region 2518 may includea ring 2512 attached to the spool 2566. In one example, the ring 2512may be formed from an elastically compliant material, such as anengineered plastic for example, polyetheretherkeone having approximatelytwenty percent carbon fiber filler. It shall be appreciated, however,that other generally elastic compliant materials may also be employed.

FIG. 25B is an exploded view of the spool 2566 with the elasticallycompliant ring 2512 shown removed from the spool 2566. The elasticallycompliant ring 2512 impacts the stop 2510 in the valve housing 2519 uponclosing the valve 2530. The elastically compliant ring 2512 deformselastically upon impacting the stop 2510 to absorb at least a portion ofthe impact energy upon closing the valve 2530. The elastically compliantportion of the spool 2566 may be formed by over-molding the elasticallycomplaint ring 2512 to the spool 2566. The elastically compliant ring2512 may be secured to the spool 2566 by providing the ring 2512 with atleast one inwardly extending boss 2516 that engages a correspondingaperture 2517 formed in the spool 2566. It should be noted, however,that the ring 2512 may be secured to the spool 2566 in other ways aswell. For example, the compliant ring 2512 may engage an annularcircumferential slot formed in the spool 2566.

With reference to FIG. 26, a valve manifold 2620 employing the co-linearvalve arrangement, such as shown in FIG. 1A, may be integrated with apump assembly 2610 for supplying pressurized fluid to a series of valves2630. This arrangement minimizes the manifold volume, which in turn mayimprove the overall operating efficiency of a hydraulic system thatincludes the pump assembly 2610. The pump assembly 2610 may include anyof a variety of known fixed displacement pumps, including but notlimited to, gear pumps, vane pumps, axial piston pumps, and radialpiston pumps. The pump assembly 2610 may include a pump input shaft 2612for driving the pump assembly 2610.

The valve manifold 2620 may include multiple hydraulically actuatedspool valves 2630. Each of the valves 2630 may include a generallycylindrical-shaped hollow sleeve 2664 that is fixed relative to themanifold 2620, and a generally cylindrical-shaped spool 2666 that isslideably disposed around the outside of the sleeve 2664. The spools2666 are free to move back and forth over a portion of the length of thesleeve 2664 between an open position and a closed position.

The sleeve 2664 and the spool 2666 each may include a series of orificesthat extend through the walls of the respective components. The spool2666 includes a series of orifices 2680 and the sleeve 2664 includes aseries of orifices 2682. The orifices 2680 and 2682 are generallyarranged in a common pattern to enable the orifices 2680 in the spool2666 to be generally aligned with the orifices 2682 in the sleeve 2664when the spool 2666 is positioned in the open position relative to thesleeve 2664. FIG. 26 illustrates the spool 2666 positioned in the closedposition, where the orifices 2680 and 2682 are generally misaligned withone another to substantially restrict fluid communication between thespool 2666 and the sleeve 2664. The valves 2630 may each employ abiasing member, illustrated as a return spring 2606, for moving thespool 2666 from the open position to the closed position.

Extending from the pump 2610 is a pump input shaft 2612. The pump inputshaft 2612 may extend lengthwise through a plenum 2614 formed by theinterconnected valve sleeves 2664 of the individual valves 2630. An end2616 of the pump input shaft 2612 extends through an end cap 2618 of themain-stage manifold 2620, and may be connected to an external powersource, such as an engine, electric motor, or another power sourcecapable of outputting a rotational torque. The end cap 2618 may beattached to a housing 2619 of the manifold 2620, and may include abearing 2621, for example, a needle bearing, roller bearing, or sleevebearing, for rotatably supporting the end 2616 of the pump input shaft2612.

The valves 2630 may be hydraulically actuated by a solenoid operatedpilot valve 2662. The pilot valve 2662 may be fluidly connected to apressure source, such as a pump 2660. When opened, the pilot valve 2662allows pressurized fluid from the pump 2660 to flow through the pilotvalve 2662 to the valve 2630. The pressurized fluid from the pilot valve2662 causes the spool 2666 of the valve 2630 to move to the openposition, thereby allowing pressurized fluid to flow from the pump 2610through the valve 2630 to a hydraulic load. Closing the pilot valve 2662stops the flow of pressurized fluid to the valve 2630, thereby allowingthe return spring 2606 to move the spool 2666 of the valve 2630 back tothe closed position.

The pump assembly 2610 may be configured to allow fluid to enter thepump assembly 2610 through an inlet passage 2627. The inlet passage 2627may be positioned at any of a variety of locations on the pump assembly,including but non limited to, on an outer circumference 2623 of the pumpassembly 2610, on a side 2625 of the pump assembly 2610 opposite thevalve manifold 2620, or any other suitable location. For purposes ofdiscussion, the inlet passage 2627 is shown in FIG. 26 arranged alongthe outer circumference 2623 of the pump. The fluid enters the pumpassembly 2610 through the inlet passage 2627 and travels radially inwardas the fluid passes through the pump assembly 2610. Pressurized fluidmay exit the pump assembly 2610 through one or more discharge ports 2628arranged along a side 2626 of the pump assembly 2610. The pressurizedfluid may be discharged from the pump assembly into the plenum 2614formed by the interconnected sleeves 2664 of the valves 2630. Thepressurized fluid can travel along an annular passage 2625 formedbetween an inner wall 2627 of the sleeves 2664 and the input shaft 2612to the respective valves 2630. Actuating one or more of the valves 2630to the open position allows the pressurized fluid to pass through theorifices 2680 in the spool 2666 and the orifices 2682 in the sleeve 2664to an exit port 2629 of the valve 2630.

FIG. 27 shows a pump assembly 2710 integrated into a valve manifold 2720employing the split collinear valve arrangement shown in FIG. 5. Thisarrangement also minimizes the manifold inlet volume, which in turn mayimprove the overall operating efficiency of a hydraulic system. In thisconfiguration, the pump assembly 2710 is arranged between two sets ofvalves 2730. Arranging the pump assembly 2710 between the valves 2730may require an inlet 2727 of the pump assembly 2710 to be positionedalong an outer circumference 2723 of the pump assembly 2710. However,depending on the size and configuration of the pump assembly 2710, itmay also be possible to position the pump inlet 2727 at another locationon the pump.

The valve manifold 2720 may include multiple hydraulically actuatedspool valves 2730. Each of the valves 2730 may include a generallycylindrical-shaped hollow sleeve 2764 that is fixed relative to themanifold 2720, and a generally cylindrical-shaped spool 2766, which isslideably disposed around the outside of the sleeve 2764. The spools2766 are free to move back and forth over a portion of the length of thesleeve 2764 between an open position and a closed position.

The sleeve 2764 and the spool 2766 each may include a series of orificesthat extend through the walls of the respective components. The spool2766 includes a series of orifices 2780 and the sleeve 2764 includes aseries of orifices 2782. The orifices 2780 and 2782 are generallyarranged in a common pattern to enable the orifices 2780 in the spool2766 to be generally aligned with the orifices 2782 in the sleeve 2764when the spool 2766 is positioned in an open position relative to thesleeve 2764. The valves 2730 may each employ a biasing member,illustrated as a return spring 2706, for moving the spool 2766 from theopen position to the closed position.

The valves 2730 may be hydraulically actuated by a solenoid operatedpilot valve 2762. The pilot valve 2762 may be fluidly connected to apressure source, such as a pump 2760. When opened, the pilot valve 2762allows pressurized fluid from the pump 2760 to flow through the pilotvalve 2762 to the valves 2730. The pressurized fluid from the pilotvalve 2762 causes the spool of the valve 2730 to move to the openposition, thereby allowing pressurized fluid to flow from the pumpassembly 2710 through the valves 2730 to a hydraulic load. Closing thepilot valve 2762 stops the flow of pressurized fluid to the valve andallows the return spring 2706 to move the spool 2766 back to the closedposition.

The pump assembly 2710 may include a pump input shaft 2712 that extendsoutward from at least one side of the pump assembly 2710. The pump inputshaft 2712 extends lengthwise through a plenum 2714 formed by theinterconnected valve sleeves 2764 of the individual valves 2730. An end2716 of the pump input shaft 2712 extends through an end cap 2718 of themanifold 2720 and may be rotatably supported by a bearing 2721, whichmay include, for example, a needle bearing, roller bearing, or sleevebearing. The end cap 2718 may be attached to the housing 2719 of themanifold 2720 and may include the bearing 2721. The end 2716 of the pumpinput shaft 2712 may be exposed and connected to an external powersource, such as an engine, electric motor, or another power sourcecapable of outputting a rotational torque. The pump assembly 2710 mayalso be configured to have the pump input shaft 2712 extend from bothsides of the pump assembly 2710, in which case an opposite end 2731 ofthe pump input shaft 2712 may be rotatably supported by a bearing 2722mounted to a manifold end cap 2729 that is attached to the manifoldhousing 2719.

Fluid enters the pump assembly 2710 through the pump inlet 2727 andtravels radially inwardly as the fluid passes through the pump assembly2710. Pressurized fluid may exit the pump assembly 2710 through one ormore discharge ports 2728 arranged along opposite sides 2726 and 2727 ofthe pump assembly 2710. The pressurized fluid may be discharged from thepump assembly 2710 into the plenum 2714 formed by the interconnectedsleeves 2764 of the valves 2730. The pressurized fluid can travel alongan annular passage 2725 formed between the inner wall 2727 of thesleeves 2764 and the pump input shaft 2712 to the respective valves2730. Actuating the valve 2730 to the open position allows thepressurized fluid to pass through the orifices 2780 in the spool 2766and the orifices 2782 in the sleeve 2664 to an exit port 2729 of thevalves 2730.

FIGS. 28A-28B illustrate a manifold 2820 for controlling thedistribution of pressurized fluid to multiple hydraulic loads havingvariable flow and pressure requirements. The manifold 2820 includes apair of valves 2830 and 2832 that employ a single sleeve 2864 and asingle spool 2866. Although the manifold 2820 is depicted in FIGS. 28Aand 28B as having two valves 2830 and 2832, it shall be appreciated thatin practice the manifold 2820 may include more valves depending, atleast in part, on the requirements of the particular application.

Each of the valves 2830 and 2832 share the generally cylindrical-shapedhollow sleeve 2864 that is fixed relative to the manifold 2820, and thegenerally cylindrical-shaped spool 2866, which is slideably disposedaround the outside of the sleeve 2864. The spool 2866 is free to moveback and forth over a portion of the length of the sleeve 2864 between afirst position and a second position.

The sleeve 2864 and the spool 2866 each may include a series of orificesthat extend through the walls of the respective components. The spool2866 includes a series of orifices 2880 and the sleeve 2864 includes aseries of orifices 2882. The orifices 2880 of the sleeve 2864 thatcorrespond with orifices 2882 of the spool 2866 for the valve 2830 aredesignated as Set 1, and the orifices 2880 of the sleeve 2864 thatcorrespond with orifices 2882 of the spool 2866 for the valve 2832 aredesignated as Set 2. The spool 2866 is movable axially relative to thesleeve 2864 between the first position and the second position. Thespool 2866 allows fluid to pass from the interior region of the sleeve2864 to the exit port 2842 of valve 2830 when the spool is in the firstposition (FIG. 28A), and the spool 2866 allows fluid to pass from theinterior region of the sleeve 2864 to the exit port 2844 of the valve2832 when the spool is in the second position (FIG. 28B). The orifices2880 and 2882 of Set 1 (i.e., valve 2830) are generally arranged in acommon pattern to enable the orifices 2880 in the spool 2866 to begenerally aligned with the orifices 2882 in the sleeve 2864 when thespool 2866 is positioned in the first position (FIG. 28A). Similarly,the orifices 2880 and 2882 of Set 2 (i.e., valve 2832) are generallyarranged in a common pattern to enable the orifices 2880 in the spool2866 to be generally aligned with the orifices 2882 in the sleeve 2864when the spool 2866 is position in the second position (FIG. 28B). Withthe spool 2866 arranged in the first position (FIG. 28A), the orifices2880 and 2882 of Set 2 (i.e., valve 2832) are misaligned such that thespool 2866 of the valve 2832 is substantially fluidly disconnected fromthe sleeve 2864 of the valve 2832. With the spool 2866 arranged in thesecond position (FIG. 28B), the orifices 2880 and 2882 of Set 1 (i.e.,valve 2830) are misaligned such that the spool 2866 of the valve 2830 issubstantially fluidly disconnected from the sleeve 2864 of the valve2830.

The spool 2866 is depicted in FIG. 28A in the first position, whereinthe valve 2830 is open and the valve 2832 closed. The valve 2830 may bearranged in the closed position, as shown in FIG. 28B, by sliding thespool 2866 axially relative to the sleeve 2864, which alsosimultaneously opens the valve 2832. Opening either of the valves 2830or 2832 allows pressurized fluid to pass through the valves 2830 and2832 to the respective exit ports 2842 and 2844. Closing either one ofthe valves 2830 and 2832 causes the other valve to open. Likewise,opening one of the valves 2830 and 2832 causes the other valve to close.

Manifold 2820 may also include a pilot valve 2862 for actuating thespool 2866 between the second position and the first position. Thevalves 2830 and 2832 may be hydraulically actuated by means of the pilotvalve 2862, which may be a solenoid operated pilot valve. The pilotvalve 2862 may include an inlet port 2863 fluidly connected to apressure source. The pilot valve 2862 may be selectively activated toallow fluid pressure to be applied to an end 2865 of the spool 2866 tomove the spool from the second position (FIG. 28B), in which valve 2832is open and valve 2830 is closed, to the first position (FIG. 28A), inwhich valve 2830 is opened and valve 2832 is closed. The valves 2830 and2832 may also employ a biasing member, illustrated as a return spring2806, for moving the spool 2866 between the first position (FIG. 28A),where the valve 2830 is open and the valve 2832 is closed, and thesecond position (FIG. 28B), where valve 2830 is closed and the valve2832 is open.

The positioning of the spool 2866 relative to the sleeve 2864 may becontrolled by means of a stop 2811 that engages a first end 2812 of thespool 2866, or another suitable region of the spool 2866, when the spool2866 is arranged in the first position (FIG. 28A). The positioning ofthe spool 2866 relative to the sleeve 2864 may also be controlled bymeans of a second stop 2813 that engages a second end 2815 of the spool2866, or another suitable region of the spool 2866, when the spool 2866is arranged in the second position (FIG. 28B).

In one example, the spool 2866 may be moved to the first position, asillustrated in FIG. 28A, by arranging the pilot valve 2862 in an openposition, which opens the valve 2830 and closes the valve 2832.Arranging the pilot valve 2862 in the open position delivers pressurizedfluid to the cavity 2898 adjacent the end 2815 of the spool 2866. Theforce exerted by the pressurized fluid overcomes the biasing forceexerted by the return spring 2806 and displaces the spool 2866 towardthe stop 2811 and into the first position. The spool 2866 may returnedto the second position, which closes the valve 2830 and opens the valve2832 (FIG. 28B), by closing the pilot valve 2862 to depressurize thecavity 2898. This allows the biasing force exerted by the return spring2806 to slide the spool 2866 axially to the second position. Themanifold may also be configured such that arranging the pilot valve 2862in the open position opens valve 2832 and arranging the pilot valve inthe closed position opens valve 2830, provided that the return spring2806 is positioned on the other end of the spool 2866.

The valves 2830 and 2832 may be configured such that either the inner orouter member operates as the spool 2866. In the exemplary valveillustrated in FIGS. 28A and 28B, the inner member functions as thesleeve 2864 and the outer member functions as the spool 2866 (i.e., ismovable relative to the sleeve). It shall be appreciated, however, thatin practice, the inner member may be configured to operate as the spool2866 and the outer member as the sleeve 2864. Further, the valves 2830and 2832 may also be configured such that both the inner and outermembers move simultaneously relative to the valve body. This latterconfiguration may produce faster valve actuation speeds, but may do soat the risk of increased complexity and cost.

Although the flow of pressurized fluid is described as passing radiallyoutward through the exemplary valves 2830 and 2832 when arranged in theopen position, it shall be appreciated that the main-stage manifold mayalso be configured such that the flow passes radially inward. In thatcase, the passages designated as the respective exit ports 2842 and 2844would operate as an inlet port, and the passage designated as the inletport 2842 would operate as an exit port. The direction in which thepressurized fluid passes through the valves 2830 and 2832 is notdependent on whether the inner or outer valve member operate as thespool, or whether both members are moveable relative to one another whenthe valves are actuated.

The valves 2830 and 2832 and the pilot valve 2862 may have separatepressure supplies or may share a common pressure source. In theexemplary manifold configuration illustrated in FIGS. 28A and 28B, thevalves 2830 and 2832, and the pilot valve 2862, are shown sharing acommon pressure source. The pressurized fluid for supplying both thevalves 2830 and 2832, and the pilot valve 2862, enters the main-stagemanifold through an inlet port 2842. The inlet port 2842 is fluidlyconnected to the sleeve 2864.

The valves 2830 and 2832 may be connected in series to form an elongatedplenum 2823. Fluidly connected to a downstream end of the sleeve 2864 ofthe valve 2832 is a pilot manifold 2825. The pilot manifold 2825includes a pilot supply passage 2827 through which a portion ofpressurized fluid may be bled from the main-stage fluid supply anddelivered to the pilot valve 2862. The inlet port 2863 of the pilotvalve 2862 may be fluidly connected to the pilot supply passage 2827.

The pilot manifold 2825 may include a check valve 2870. The check valve2870 operates to control the flow of pressurized fluid delivered to thepilot manifold 2825, and also prevent fluid from back flowing from thepilot manifold 2825 to the plenum 2823. The check valve 2870 may haveany of a variety of configurations. An example of one such configurationis illustrated in FIGS. 28A and 28B, where a ball check valve isutilized to control the flow of fluid to and from the pilot manifold2825. The check valve 2870 includes a ball 2872 that selectively engagesan inlet passage 2874 of the pilot manifold 2825. A spring 2876 may beprovided for biasing the ball 2872 into engagement with the inletpassage 2874 of the pilot manifold 2825. When the pressure drop acrossthe check valve 2870 exceeds the biasing force exerted by the spring2876, the ball 2872 will disengage the inlet passage 2874 of the pilotmanifold 2825 to allow pressurized fluid to flow from the plenum 2823 tothe pilot manifold 2825. The rate at which fluid flows from thehydraulic manifold 2820 to the pilot manifold 2825 is dependent on thepressure drop across the check valve 2870. The greater the pressuredrop, the higher the flow rate. In instances where the pressure dropacross the check valve 2870 is less then the biasing force of the spring2876, or the pressure within the pilot manifold 2825 exceeds thepressure within the hydraulic manifold 2820, the check valve ball 2872will engage the inlet passage 2874 of the pilot manifold 2825 to preventflow from passing through the check valve 2870 in either direction. Thespring rate of the spring 2876 can be selected so as to prevent thecheck valve 2870 from opening until a desired pressure drop across thecheck valve 2870 is achieved.

The pilot manifold 2825 may also include an accumulator 2890 for storingpressurized fluid used to actuate the valves 2830 and 2832. Theaccumulator 2890 may have any of a variety of configurations. Forexample, a fluid reservoir 2892 for receiving and storing pressurizedfluid may be included. The reservoir 2892 may be fluidly connected tothe pilot manifold 2825. The accumulator 2890 may include a moveablepiston 2894 positioned within the reservoir 2892. The positioning of thepiston 2894 within the reservoir 2892 can be adjusted to selectivelyvary the volume of the reservoir 2892. A biasing mechanism 2896, such asa coil spring, urges the piston 2894 in a direction that tends tominimize the volume of the reservoir 2892. The biasing mechanism 2896exerts a biasing force that opposes the pressure force exerted by thepressurized fluid present within the pilot manifold 2825. If the twoopposing forces are unbalanced, the piston 2894 will be displaced toeither increase or decrease the volume of the reservoir 2892, therebyrestoring the balance between the two opposing forces. In at least somesituations, the pressure level within the reservoir 2892 corresponds tothe pressure within the pilot manifold 2825. If the pressure forcewithin the reservoir 2892 exceeds the opposing force generated by thebiasing mechanism 2896, the piston 2894 will be displaced toward thebiasing mechanism 2896, thereby increasing the volume of the reservoir2892 and the amount of fluid that can be stored in the accumulator 2890.As the reservoir 2892 continues to fill with fluid, the opposing forcegenerated by the biasing mechanism 2896 will also increase to the pointat which the biasing force and the opposing pressure force exerted fromwithin the reservoir 2892 are substantially equal. The volumetriccapacity of the reservoir 2892 will remain substantially constant whenthe two opposing forces are at equilibrium. On the other hand, actuatingthe pilot valve 2862 will generally cause the pressure level within thepilot manifold 2825 to drop below the pressure level within thereservoir 2892. This coupled with the fact that the pressure forcesacross the piston 2894 are now unbalanced will cause fluid stored in thereservoir 2892 to be discharged to the pilot manifold 2825 for use inactuating the valves 2830 and 2832.

FIG. 29A illustrates a manifold 2920 that includes a valve 2930. Thevalve 2930 employs a spool 2966 that includes an actuator 2909 having anactuation surface 2910. The valve 2930 may be a hydraulically actuatedspool valve including a generally cylindrical-shaped hollow sleeve 2964that is fixed relative to the manifold 2920, and the generallycylindrical-shaped spool 2966, which is slideably disposed around theoutside of the sleeve 2964. The spool 2966 is free to move back andforth over a portion of the length of the sleeve 2964 between an openposition and a closed position. The sleeve 2964 and the spool 2966 eachmay include a series of orifices that extend through the walls of therespective components, where the spool 2966 includes a series oforifices 2982 and the sleeve 2964 includes a series of orifices 2980.

The valve 2930 may be hydraulically actuated by an actuating device,such as a pilot valve, for moving the spool 2966 from the closedposition to the open position. The valve 2930 may also employ a biasingmember, illustrated as a return spring 2906, for moving the spool 2866from the open position to the closed position. Arranging the pilot valvein an open position causes a flow of pressurized fluid to be deliveredto a cavity 2998 that is in fluid communication with actuation surface2910. The pressurized fluid exerts a generally axial force against theactuation surface 2910 of the spool 2966, which tends to displace thespool 2966 axially relative to the sleeve 2964 in a direction toward thereturn spring 2906. Closing the pilot valve depressurizes the cavity2998, thereby allowing the return spring 2906 to return the spool 2966to the closed position.

The actuator 2909 may be located at an end portion 2914 of the spool2966 opposite the return spring 2906. The orifice 2982 of the spool 2966may include a longitudinal axis A-A, where a dimension L that representsthe length of the orifice 2982 may be measured substantially parallel tothe axis A-A. The actuation surface 2910 may also include a thicknessT′, where the thickness T′ may be less than the dimension L of theorifice 2982.

A wall thickness T of the spool 2966 may be greater than wall thicknessT′ of the actuation surface 2910, and in one example the wall thicknessT may also be substantially equal to the dimension L. A wall thickness Tmay be selected to minimize deflection of the wall that may occur as aresult of the pressure drop across the spool 2966. For example, thepressure within the interior region of sleeve 2964 may be higher thanthe pressure surrounding the outer periphery of the spool 2966. Thepressure drop occurring across the spool 2966 may cause the wall of thespool to deflect outward. The amount of deflection is dependent on avariety of factors, including but not limited to, the wall thickness T,the material properties of the spool, and the magnitude of the pressuredrop occurring across the spool. The wall deflection can be minimizedby, among other things, increasing the wall thickness T.

In at least one example, the spool 2966 may be actuated by exerting aforce on a portion of the wall thickness T, such as, for example, thewall thickness T′. The magnitude of the force applied to the spool 2966is generally a function of the area of the actuation surface 2910 andthe magnitude of the applied pressure. Increasing either the appliedpressure or the surface area will generally produce a correspondingincrease in the axial actuating force applied to the spool 2966. Themagnitude of the actuating force can be controlled by adjusting thethickness T′ of the actuation surface 2910.

The actuation surface 2910 may be located adjacent an outer surface 2914of the spool 2966. Alternatively, as shown in FIG. 29B, an actuationsurface 2910′ may be located adjacent the inner surface 2916 of thespool 2966. Referring to both FIGS. 29A and 29B, the actuation surfaces2910 (FIG. 29A) and 2910′ (FIG. 29B) provide an area against whichpressurized fluid can exert an axial force on the spool 2966 to slidethe spool into the open position. Pressure applied against the actuationsurfaces 2910 and 2910′ urge the spool 2966 into the open position.

FIG. 30 is an illustration of a manifold 3020 including a valve 3030.The valve 3030 may be a hydraulically actuated spool valve including agenerally cylindrical-shaped hollow sleeve 3064 that is fixed relativeto the manifold 3020, and a generally cylindrical-shaped spool 3066,which is slideably disposed around the outside of the sleeve 3064. Thespool 3066 is free to move back and forth over a portion of the lengthof the sleeve 3064 between an open position and a closed position. Thesleeve 3064 and the spool 3066 each may include a series of orificesthat extend through the walls of the respective components, where thespool 3066 includes a series of orifices 3080 and the sleeve 3064includes a series of orifices 3082. The spool 3066 is shown arranged inthe closed position in FIG. 30, wherein the orifices 3080 of the spool3066 are substantially fluidly disconnected from the orifices 3082 ofthe sleeve 3064. Placing the spool 3066 in the open position (i.e., bysliding the spool to the left in FIG. 30) fluidly connects the orifices3080 in the spool with the orifices 3082 in the sleeve 3064.

The valve 3030 may include an actuator 3008 arranged at a distal end ofthe spool 3066 for moving the spool 3066 between the open position andthe closed position. The actuator 3008 may have a similar configurationas the actuator 2909 shown in FIG. 29B. In one example, the spoolactuator 3008 may be a generally annular ring that may be fixedlyattached to the spool 3066 by means of a connector 3010. The actuator3008 provides an actuating surface 3011 against which an actuating forcecan be applied to urge the spool 3066 from the closed position to theopen position. The valve 3030 may also included a biasing member,illustrated as a return spring 3006, for moving the spool 3066 from theopen position to the closed position.

The spool actuator 3008 may include a wall thickness T′. Similar to theillustration in FIGS. 29A-29B, the thickness T′ of the spool actuator3008 may be less than a wall thickness T of the spool 3066 in order toachieve a desired actuating force while allowing the spool 3066 tomaintain a desired wall thickness T across the portion of the spool 3066including the orifices 3080. The force required to actuate the spool3066 may be varied by changing the thickness T′ of the spool actuator3008. This configuration allows the wall thickness T′ of the spoolactuator 3008 to be sized to obtain a desired actuation force and thewall thickness T of the spool 3066 to be sized to minimize outwarddeflection of the spool 3066.

The spool actuator 3008 may be connected to the spool 3066 using theconnecting member 3010. The connecting member 3010 may include a lip3014 that engages a corresponding lip 3016 on the spool actuator 3008,and a second lip 3018 that engages a corresponding lip 3019 on the spool3066 Other means that may be used to connect the connecting member 3010to the spool 3066 and the spool actuator 3008, include but are notlimited to, brazing, welding, and gluing. The type of connection methodemployed will depend at least in part on the type of materials used andthe structural requirements of the connection.

Manifold 3020 may include an actuation chamber 3012 that is in fluidcommunication with the actuation surface 3010 of the spool actuator3008. The spool actuator 3008 may be at least partially located withinthe actuation chamber 3012. An actuation flow port 3014 may also beprovided for supplying pressurized fluid to the actuation chamber 3012for actuating the valve. The actuation flow port 3014 may be fluidlyconnected to a pressure source, such as a pump. The actuation chamber3012 receives fluid pressure from the actuation flow port 3014. Thefluid pressure in the actuation chamber 3012 provides the actuationforce used to move the spool 3066 axially within the manifold 3020 tothe open position. The actuation force may be exerted on the spoolactuator 3008 by the pressurized fluid located within the actuationchamber 3012 to displace the spool 3066 toward the open position.Pressurized fluid may be released from the actuation chamber 3012 toallow the return spring 3006 to urge the spool 3066 into the closedposition.

Referring to FIG. 31A, an alternative configuration of a spool actuator3108 includes at least one pin 3102 that may be in communication with adistal actuation end 3113 of a spool 3166. The pins 3102 may be housedwithin a spool actuator housing 3106 that acts as a guide for the pins3102 to slide axially within the actuator housing. An actuation chamber3112 is located adjacent one end of the pin 3102. A least a portion ofthe pin 3102 is in fluid communication with the actuation chamber 3012.

The actuation chamber 3112 receives pressurized fluid from a pressuresource. The pressurized fluid provides the actuation force used to movethe spool 3166 axially within the manifold 3120 to an open position. Theactuation force may be exerted on the pins 3102 by the pressurized fluidlocated within the actuation chamber 3112. The actuation force exertedon the ends of the pins 3102 urges the spool 3166 toward the openposition. A biasing member, illustrated as a return spring 3106, may beprovided to urge the spool 3166 back to the closed position.

In one exemplary configuration, as shown in FIG. 31B, four pins 3102 maybe arranged within the actuator housing 3106. The actuator housing 3106may be fixedly attached to a valve housing 3115. The actuator housing3106 may also be configured as part of the valve housing 3115. It shouldbe noted that while FIG. 31B illustrates fours pins 3102 arranged withinthe actuator housing 3106 and located equidistant from one another,other configurations using a different number of pins or a differentdistribution may be used as well. For example, the pin housing 3102 mayinclude five or more pins 3102 that are spaced at unequal distances fromone another.

With reference to FIGS. 1 and 32, hydraulic manifold 20 (see FIG. 1A)may be integrated with a pump 3212 to form an integrated fluiddistribution module 3210. Integrating the various devices may improvesystem efficiency by reducing the volume of compressible fluid presentwithin the hydraulic system, which in turn may reduce the total amountof work required to compress the fluid present within the hydraulicsystem.

For clarity, those components and features of the fluid distributionmodule 3210 that are in common with the hydraulic manifold 20 areidentified using like reference numbers in FIG. 32. Fluid distributionmodule 3210 may include the control valves 30, 32, 34 and 36 ofhydraulic manifold 20. The control valves 30, 32, 34 and 36 may bedisposed in a common housing 3212. Exit ports 44, 46, 48 and 50 of thecontrol valves 30, 32, 34 and 36, respectively, are accessible fromoutside housing 3212 for fluidly connecting various hydraulic loads (notshown) to fluid distribution module 3210. One or more of the controlvalves may also employ the solenoid operated pilot valve for actuatingthe respective control valve.

Pressurized fluid for driving various hydraulic loads (not shown)fluidly connected to the control valves may be provided by a fixeddisplacement pump 3214. Pump 3214 may include any of a variety of knownfixed displacement pumps, including but not limited to, gear pumps, vanepumps, axial piston pumps, and radial piston pumps. The pump 3214includes a drive shaft 3216 for driving the pump. The drive shaft 3216can be connected to an external power source, such as an engine,electric motor, or another power source capable of outputting arotational torque. An inlet port 3218 of the pump 3214 may be fluidlyconnected to a fluid reservoir (not shown). The inlet port 42 of thehydraulic manifold may be fluidly connected to a discharge port 3220 ofpump 3214.

Although a single pump 3214 is illustrated for purposes of discussion,fluid distribution module 3210 may include multiple pumps, each havingtheir respective discharge ports fluidly connected to a common fluidnode from which the individual fluid circuits can be supplied withpressurized fluid. The multiple pumps may be fluidly connected, forexample, in parallel to achieve higher flow rates, or in series, such aswhen higher pressures for a given flow rate are desired.

With regard to the processes, systems, methods, etc. described herein,it should be understood that, although the steps of such processes, etc.have been described as occurring according to a certain orderedsequence, such processes could be practiced with the described stepsperformed in an order other than the order described herein. It furthershould be understood that certain steps could be performedsimultaneously, that other steps could be added, or that certain stepsdescribed herein could be omitted. In other words, the descriptions ofprocesses herein are provided for the purpose of illustrating certainembodiments, and should in no way be construed so as to limit theclaimed invention.

It is to be understood that the above description is intended to beillustrative and not restrictive. Many embodiments and applicationsother than the examples provided would be apparent to those of skill inthe art upon reading the above description. The scope of the inventionshould be determined, not with reference to the above description, butshould instead be determined with reference to the appended claims,along with the full scope of equivalents to which such claims areentitled. It is anticipated and intended that future developments willoccur in the arts discussed herein, and that the disclosed systems andmethods will be incorporated into such future embodiments. In sum, itshould be understood that the invention is capable of modification andvariation and is limited only by the following claims.

All terms used in the claims are intended to be given their broadestreasonable constructions and their ordinary meanings as understood bythose skilled in the art unless an explicit indication to the contraryin made herein. In particular, use of the singular articles such as “a,”“the,” “said,” etc. should be read to recite one or more of theindicated elements unless a claim recites an explicit limitation to thecontrary.

What is claimed is:
 1. A valve comprising: a valve body; several firstvalve members, each including a first step and each including a firstorifice adjacent the respective first step and configured within andfixed relative to the valve body; and several second valve members, eachincluding a second step and a second orifice adjacent the respectivesecond step configured within and movable relative to the valve body,the second valve members movable relative to the first valve membersbetween open positions, in which the first orifices are fluidlyconnected with the second orifices, and a closed position, in which thefirst orifices are substantially fluidly disconnected from the secondorifices, wherein the first and second steps are fluidly connected to arespective first orifice and a respective second orifice andsubstantially fluidly disconnected from the remaining orifices when thesecond valve members are in the closed position, and the first andsecond steps are fluidly connected to the first and second orifices whenthe respective second valve member is in the open position; wherein thefirst valve members define a portion of a plenum; wherein the firstorifices are fluidly connected to the plenum; and wherein the plenum isfluidly connected to a plurality of valves.
 2. The valve of claim 1,wherein the first and second steps at least partially define a fluidpathway between the first and second orifices when the second valvemembers are in the open position.
 3. The valve of claim 1, furthercomprising a biasing member in communication with the second valvemembers, the biasing member urging the second valve members toward theclosed position.
 4. The valve of claim 3, wherein the first steps arepositioned on a side of the respective first orifice furthest away fromthe biasing member and facing the second steps, and the second steps arelocated on a side of the first orifices nearest the biasing member whenthe second valve members are in the closed position.
 5. The valve ofclaim 3, wherein the first steps are positioned on a side of the firstorifices closest to the biasing member and the second steps are locatedon a side of the first orifices furthest away from the biasing memberwhen the second valve members are in the closed position.
 6. The valveof claim 3, wherein the second steps are positioned on a side of thesecond orifices furthest away from the biasing member and the firststeps are located on a side of the second orifices nearest the biasingmember when the second valve members are in the closed position.
 7. Thevalve of claim 3, wherein the second steps are positioned on a side ofthe second orifices closest to the biasing member and the first stepsare located on a side of the second orifices furthest away from thebiasing member when the second valve members are in the closed position.8. A hydraulic valve manifold comprising: at least two valve bodiesinterconnected to form a mainstage manifold, each valve body comprising:a plurality of first valve members, each including a first step and arespective first orifice adjacent the first steps configured within andfixed relative to the valve body, and a plurality of second valvemembers, each including a second step and a respective second orificeadjacent the second steps configured within and movable relative to thevalve body, the second valve members movable relative to the first valvemembers between open positions, in which the first orifices are fluidlyconnected with the second orifices, and a closed position, in which thefirst orifices are substantially fluidly disconnected from the secondorifices, wherein the first and second steps are fluidly connected to arespective first orifice and a respective second orifice andsubstantially fluidly disconnected from the remaining orifices when thesecond valve members are in the closed position, and the first andsecond steps are fluidly connected to the first and second orifices whenthe respective second valve member is in the open position; wherein eachof the first valve members defines a portion of a plenum; wherein theplenum extends between and is fluidly connected to the first orifice ofeach of the at least two valve bodies; and wherein the mainstagemanifold is configured to fluidly control at least a first hydraulicload and a second hydraulic load.
 9. The hydraulic valve manifold ofclaim 8, wherein the first hydraulic load includes a first variable flowand a first predetermined pressure, and wherein the second hydraulicload includes a second variable flow and a second predeterminedpressure, the second variable flow is at least one of the same anddifferent than the first variable flow and the second predeterminedpressure is at least one of the same and different than the firstpredetermined pressure.
 10. The hydraulic valve manifold of claim 8,wherein movement of the second valve members to the open positionfluidly connects the first orifices with the second orifices.
 11. Thehydraulic valve manifold of claim 8, wherein movement of the secondvalve members to the closed position substantially fluidly disconnectsthe first orifices from the second orifices.
 12. The hydraulic valvemanifold of claim 8, wherein the first and second steps at leastpartially define a fluid pathway between the first and second orificeswhen the second valve members are in the open position.
 13. Thehydraulic valve manifold of claim 8, further comprising a biasing memberin communication with the second valve members, the biasing memberurging the second valve members toward the closed position.
 14. Thehydraulic valve manifold of claim 13, wherein the second steps arepositioned on a side of the second orifices closest to the biasingmember and the first steps are located on a side of the second orificesfurthest away from the biasing member when the second valve members arein the closed position.
 15. The hydraulic valve manifold of claim 13,wherein the first steps are positioned on a side of the first orificesfurthest away from the biasing member and the second steps are locatedon a side of the first orifices nearest the biasing member when thesecond valve members are in the closed position.
 16. The hydraulic valvemanifold of claim 13, wherein the first steps are positioned on a sideof the first orifices closest to the biasing member and the second stepsare located on a side of the first orifices furthest away from thebiasing member when the second valve members are in the closed position.17. The hydraulic valve manifold of claim 13, wherein the second stepsare positioned on a side of the second orifices furthest away from thebiasing member and the first steps are located on a side of the secondorifices nearest the biasing member when the second valve members are inthe closed position.